CN111271254B - Oil supply structure for compressor and compressor with same - Google Patents
Oil supply structure for compressor and compressor with same Download PDFInfo
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- CN111271254B CN111271254B CN201811480168.1A CN201811480168A CN111271254B CN 111271254 B CN111271254 B CN 111271254B CN 201811480168 A CN201811480168 A CN 201811480168A CN 111271254 B CN111271254 B CN 111271254B
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- supply structure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0284—Constructional details, e.g. reservoirs in the casing
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Abstract
The invention discloses an oil supply structure with a compressor, which comprises: the crankshaft is vertically arranged and provided with a central hole; the oil pump spare, the cooperation of oil pump spare is in the lower part of centre bore, the periphery wall of oil pump spare with be equipped with the clearance between the internal perisporium of centre bore, oil pump spare can be relative the crankshaft rotates. According to the oil supply structure for the compressor, on the premise of better thinning the diameter of the crankshaft, the oil supply quantity of each part of the compressor is increased, and the efficiency and the reliability of the compressor are improved.
Description
Technical Field
The invention relates to the field of refrigeration equipment, in particular to an oil supply structure for a compressor and the compressor with the oil supply structure.
Background
For the reciprocating refrigeration compressor, the oil supply system is mainly responsible for lubricating all moving parts of the compressor, reducing the abrasion of all parts during operation and simultaneously reducing the working temperature of the compressor so as to achieve the purposes of improving the reliability of the compressor and prolonging the service life of the compressor.
The oil supply system of the existing reciprocating refrigeration compressor is limited by structural design and processing technology, and generally adopts a centrifugal oil pumping structure and a spiral viscous oil pumping structure comprehensively. The oil supply structure comprises a crankshaft, an oil pump part, a rack, a stator, a rotor, a shell and an oil pool. The crankshaft is generally provided with a centrifugal pump oil section and a spiral viscous pump oil section, and the oil pump part comprises an oil pump shell and an oil feeding blade. The upper end of the oil pump component is fixed at the lower end of the crankshaft, and the lower end of the oil pump component is immersed in the oil pool. When the reciprocating refrigeration compressor works, the crankshaft rotates clockwise at a certain rotating speed under the driving of the rotor, refrigerating machine oil in the oil pool is pumped to the upper end of the oil pump part under the action of rotating centrifugal force, then rises to the inlet of the spiral viscous pump oil section along the centrifugal pump oil section on the crankshaft, continues to rise to the upper end of the crankshaft along the spiral viscous pump oil section, and finally reaches each part needing lubrication in the compressor. Because the oil supply height of the oil section of the crankshaft centrifugal pump is in square relation with the diameter of the crankshaft, the influence of the diameter of the crankshaft is large, and after the shaft diameter of the crankshaft is thinned to a certain degree, the oil supply capacity is greatly reduced, and the normal operation of the refrigeration compressor is influenced.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art. To this end, the present invention proposes an oil supply structure for a compressor, which ensures a good oil pumping capability even in the case of a small diameter of a crankshaft.
The present invention is also directed to a compressor having the oil supply mechanism for a compressor.
An oil supply structure for a compressor according to an embodiment of the present invention includes: the crankshaft is vertically arranged and provided with a central hole; the oil pump spare, the cooperation of oil pump spare is in the lower part of centre bore, the periphery wall of oil pump spare with be equipped with the clearance between the internal perisporium of centre bore, oil pump spare can be relative the crankshaft rotates.
According to the oil supply structure for the compressor, provided by the embodiment of the invention, as the gap is formed between the oil pump piece and the central hole of the crankshaft, and the oil pump piece can rotate relative to the crankshaft, on the premise of better realizing the diameter thinning of the crankshaft, the oil supply quantity of each part of the compressor is increased, and the efficiency and the reliability of the compressor are improved.
In some embodiments, a gap width between the outer peripheral wall of the oil pumping member and the inner peripheral wall of the center hole is S, S satisfying the relation: s is more than or equal to 0.04mm and less than or equal to 0.2 mm.
In some embodiments, the outer peripheral wall of the oil pumping member is provided with a helical oil groove extending in the axial direction.
In some alternative embodiments, the helical oil groove has a width a and a depth b, and a and b satisfy the following relation: a is more than or equal to 1mm, and b is less than or equal to 1.5mm.
In some optional embodiments, the helical oil groove has an axial length L, and L satisfies the relationship: l is less than or equal to 50 mm.
In some optional embodiments, the number of the spiral oil grooves is n, and n is a positive integer less than or equal to 3.
In some alternative embodiments, the helical oil groove has a helix angle c, and c satisfies the relationship: c is more than or equal to 15 degrees.
In some embodiments, the oil pump member is provided with a lightening hole which penetrates along the axial direction, and the lower end of the lightening hole is formed into a necking.
In some embodiments, the crankshaft has an outer diameter D1, the central bore has a diameter D2, and D1 and D2 satisfy the relationship: d1 is not more than 15mm, and D2 is not less than 5mm.
In particular embodiments, the outer diameter D1 of the crankshaft and the diameter D2 of the central bore satisfy the relationship: 2/3 is not less than D2/D1 is not less than 4/5.
The compressor according to the embodiment of the present invention includes the oil supply structure for the compressor as described above.
According to the compressor provided by the embodiment of the invention, due to the oil supply structure, on the premise of ensuring light weight, better lubrication is realized, and the efficiency and the reliability of the compressor are improved.
In some embodiments, the oil pumping member includes: the oil pumping part is matched in the central hole, a gap is formed between the outer peripheral wall of the oil pumping part and the inner peripheral wall of the central hole, and the lower end surface of the oil pumping part is flush with the lower end surface of the crankshaft; the installation department, the installation department is connected the lower extreme of pump oil portion, the installation department be provided with the installation ear that the casing of compressor links to each other.
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 compressor according to an embodiment of the present invention.
Fig. 2 is a schematic structural view of an oil supply structure of an embodiment of the present invention.
Fig. 3 is a perspective view of an oil pump member of an embodiment of the present invention.
Fig. 4 is a plan view of an oil pump member of an embodiment of the present invention.
Fig. 5 is a vertical sectional view of an oil pump member of an embodiment of the present invention.
Reference numerals:
a compressor 100,
An oil supply structure 1,
A crankshaft 11, a central hole 111,
An oil pumping element 12,
An oil pumping part 121, a spiral oil groove 1211, a lightening hole 1212, a reducing opening 1213,
A mounting portion 122,
A frame 2,
A shaft hole 21,
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.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the invention. Furthermore, 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 of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
An oil supply structure 1 for a compressor according to an embodiment of the present invention will be described with reference to fig. 1 to 5.
As shown in fig. 1 and 2, an oil supply structure 1 for a compressor according to an embodiment of the present invention includes a crankshaft 11 and an oil pump member 12, the crankshaft 11 is vertically disposed, the crankshaft 11 has a central hole 111, the oil pump member 12 is fitted in a lower portion of the central hole 111, a gap is provided between an outer peripheral wall of the oil pump member 12 and an inner peripheral wall of the central hole 111, and the oil pump member 12 is rotatable relative to the crankshaft 11.
It will be understood that in the present application, there is a gap between the oil pumping element 12 and the inner wall of the central hole 111 of the crankshaft 11, and the oil pumping element 12 can rotate relative to the crankshaft 11, so that when the crankshaft 11 rotates due to the normal operation of the compressor 100, the lubricating oil can enter the central hole 111 from the gap between the oil pumping element 12 and the inner peripheral wall of the central hole 111 under the action of the pressure difference, and when the lubricating oil rises to a certain height, the lubricating oil is delivered to the rest of the components of the compressor 100 through the oil supply hole opened in the crankshaft 11. It is found through experiments that the oil pump height of the oil pump member 12 is linear with the diameter of the crankshaft 11 in the present application, whereas the oil supply height of the oil supply structure 1 is linear with the square of the diameter of the crankshaft 11 in the prior art. Therefore, the oil supply height of the oil pump piece 12 is far greater than that of the prior art, so that the oil supply quantity of each part of the compressor 100 is increased on the premise that the diameter of the crankshaft 11 is thinned, and the efficiency and the reliability of the compressor 100 are improved.
According to the oil supply structure 1 for the compressor of the embodiment of the invention, because the gap is formed between the oil pump 12 and the central hole 111 of the crankshaft 11, and the oil pump 12 can rotate relative to the crankshaft 11, on the premise of better realizing the diameter thinning of the crankshaft 11, the oil supply amount of each part of the compressor 100 is increased, and the efficiency and the reliability of the compressor 100 are improved.
In some embodiments, the gap width between the outer peripheral wall of the oil pump member 12 and the inner peripheral wall of the center hole 111 is S, which satisfies the relationship: s is more than or equal to 0.04mm and less than or equal to 0.2 mm. It is understood that the oil pumping ability of the oil pumping element 12 can be improved by experimentally investigating that the clearance between the outer peripheral wall of the oil pumping element 12 and the inner peripheral wall of the center hole 111 is controlled to be 0.04mm to 2 mm. In addition, experiments prove that when S is in the range of 0.05mm to 0.15mm, the oil pumping effect is relatively better.
It should be noted that, as shown in fig. 2, the gap width here means a single-sided dimension between the outer peripheral wall of the oil pumping element 12 and the inner peripheral wall of the center hole 111. It is of course emphasized here that the size of the gap between the oil pumping member 12 and the outer wall of the central hole 111 is not limited to the above range, and the size of the gap may be selected according to the actual size of the crankshaft 11 and the central hole 111 of the compressor 100. In addition, although the crankshaft 11 of the compressor 100 is generally cylindrical, it does not mean that the central hole 111 is necessarily a circular hole, in this application, the central hole 111 may be a circular hole or a square hole, and the oil pumping element 12 may be a cylinder or a square column, where the specific shapes of the central hole 111 and the oil pumping element 12 are not limited, and both may be selected according to actual needs.
In some embodiments, as shown in fig. 3, the outer peripheral wall of the oil pumping member 12 is provided with a spiral oil groove 1211 extending in the axial direction. Through experimental studies by the inventors, it was found that when an oil groove is present in the outer peripheral wall of the oil pumping member 12, the oil pumping capability of the oil pumping member 12 is superior to that without the oil groove. Among the various oil groove shapes, the spiral oil groove 1211 has a better oil pumping capability. Thus, the provision of the spiral oil groove 1211 spirally extending in the vertical direction on the outer peripheral wall of the oil pump member 12 can ensure the oil pumping capability of the oil supply structure 1 well, thereby ensuring good lubrication of the compressor 100. Of course, the oil groove in the outer peripheral wall of the oil pump member 12 is not limited to a spiral shape, and may be a straight groove or an arc groove extending in the vertical direction, or the like.
In some alternative embodiments, as shown in fig. 5, the spiral oil groove 1211 has a width a and a depth b, and a and b satisfy the relationship: a is more than or equal to 1mm, and b is less than or equal to 1.5mm. It can be understood that the width and depth of the spiral oil groove 1211 directly affect the oil pumping capability of the oil pumping member 12, and it is found through experiments that the oil pumping capability of the oil pumping member 12 is better when a and b are within the above range, thereby securing the lubricating effect of the compressor 100.
Preferably, a satisfies the relation of 1.5mm ≦ a ≦ 3.5mm, and b satisfies the relation of 0.5mm ≦ a ≦ 1.5mm, it should be noted that, regardless of the width and depth of the spiral oil groove 1211, the oil pumping capacity of the oil pumping element 12 cannot be guaranteed well, and through experimental studies of the inventor, it is found that when a is located within 1.5mm to 3.5mm, and b is located within 0.5mm to 1.5mm, the oil pumping amount and the oil pumping height of the oil pumping element 12 are both large. That is, when a and b satisfy the above-mentioned relational expression, the oil pumping ability of the oil pumping element 12 is strong, so that the lubricating effect of the compressor 100 is good.
Of course, in other embodiments of the present application, the value ranges of a and b are not limited to the above ranges, and the specific values of both can be specifically selected according to the size of the oil pumping member 12 and the amount of lubricating oil required by the compressor 100.
In some alternative embodiments, as shown in fig. 5, the helical oil groove 1211 has an axial length L, where L satisfies the relationship: l is less than or equal to 50 mm. It can be understood that the oil pumping element 12 is fitted in the central hole 111 and can rotate relative to the crankshaft 11, so if the length of the oil pumping element 12 is too long, the amplitude of rotation of the oil pumping element 12 is small, and the oil pumping effect is easily affected by the oil pumping element being stuck in the central hole 111. Therefore, when L is less than or equal to 50mm, the rotatable amplitude of the oil pump part 12 can be well ensured, the possibility of clamping the oil pump part 12 is reduced, and the oil pumping capacity of the oil pump part 12 is ensured. Preferably, L is more than or equal to 20mm and less than or equal to 40 mm. Of course, in other embodiments of the present application, L is not limited to the above range, and the specific value of L may be selected according to practical situations.
In some alternative embodiments, as shown in fig. 4, the number of lines of the spiral oil groove 1211 is n, and n is a positive integer less than or equal to 3. It is understood that the value of n can take 1, 2, and 3. When n is equal to 1, the oil pumping speed of the oil pumping element 12 is fast, and when n is equal to 3, the oil pumping amount of the oil pumping element 12 is large, and the number of lines of the oil sumps 1211 can be selected according to actual requirements in practical application. In addition, in the practical application process, the value of n is not limited to the above value, and any positive integer can be selected according to the practical requirement.
Here, the number of spiral lines of the spiral oil groove 1211 refers to the number of spiral lines forming the spiral oil groove 1211. The spiral oil groove 1211 is formed of one spiral line when the number of lines is 1, and 2 or 3 corresponding spiral oil grooves when the number of lines is 2 or 3.
In some alternative embodiments, as shown in FIG. 5, the spiral oil groove 1211 has a spiral angle c, and c satisfies the relationship: c is more than or equal to 15 degrees. It is understood that the spiral angle of the spiral oil groove 1211 influences the pumping speed and the pumping amount of the oil pumping member 12, and it is found through research that the pumping speed and the pumping amount of the oil pumping member 12 are high when the spiral angle is 15 ° or more. Further, c satisfies the relation: c is more than or equal to 20 degrees and less than or equal to 30 degrees. It will be understood that the excessive spiral angle of the spiral oil groove 1211 adversely affects the oil pumping effect, and thus the oil pumping effect of the oil pumping member 12 can be better secured by controlling c to be in the range of 20 to 30.
In some embodiments, as shown in fig. 5, the oil pump element 12 is provided with a weight-reducing hole 1212 that penetrates in the axial direction, and a lower end of the weight-reducing hole 1212 is formed as a constricted opening 1213. It is understood that the oil pumping member 12 having the lightening holes 1212 can reduce the mass of the oil pumping member 12 so that it can be better rotated with respect to the crankshaft 11, thereby ensuring the oil pumping effect of the oil pumping member 12. Furthermore, when the compressor 100 is stopped, not only will the respective lubricating oil flow back to the oil sump 6, but the lightening holes 1212 and the throats 1213 of the oil pumping member 12 also ensure a quick flow of lubricating oil back to the oil sump 6.
In some embodiments, as shown in FIG. 2, the crankshaft 11 has an outer diameter D1, the central bore 111 has a diameter D2, and D1 and D2 satisfy the relationship: d1 is not more than 15mm, and D2 is not less than 5mm. The larger the outer diameter of the crankshaft 11, the larger the mass of the entire compressor 100, and the outer diameter of the crankshaft 11 of the present application is 15mm or less, which realizes a lightweight design of the compressor 100. In the present application, due to the oil pump 12, the lubrication of the compressor 100 is better ensured, that is, the oil supply device of the present application also ensures the lubrication effect of the compressor 100 on the premise of realizing the lightweight design of the compressor 100, and improves the reliability of the compressor 100. Advantageously, D1 satisfies the relationship: d1 is more than or equal to 9mm and less than or equal to 14mm, and D2 is more than or equal to 6 and less than or equal to 11 mm. It is understood that too little D1 or too much D2 may result in insufficient rigidity of the crankshaft 11, and therefore, controlling D1 and D2 in the above range ensures the strength of the crankshaft 11 while ensuring the weight reduction of the crankshaft 11, thereby ensuring the reliability and portability of the compressor 100
In some specific embodiments, D1 and D2 satisfy the relationship: 2/3 is not less than D2/D1 is not less than 4/5. Therefore, the strength of the crankshaft 11 can be better ensured while the crankshaft 11 is further ensured to be light, so that the reliability and the portability of the compressor 100 are better ensured.
Of course, in the present application, the outer diameter D1 of the crankshaft 11 and the diameter D2 of the central bore 111 are not limited to the above ranges, and D1 and D2 may be selected according to specific needs.
In some embodiments, the oil pumping member 12 is injection molded from a polymeric material. Thereby, the mass of the oil pump element 12 is reduced, and the production cost of the oil pump element 12 is reduced. Of course, in the present application, the oil pumping member 12 may be produced by other materials and processes, which are not described herein by way of example.
The compressor 100 according to the embodiment of the present invention includes the foregoing oil supply structure 1 for a compressor.
According to the compressor 100 of the embodiment of the present invention, since the oil supply structure 1 is provided, on the premise of ensuring light weight, better lubrication is achieved, and the efficiency and reliability of the compressor 100 are improved.
In some embodiments, as shown in fig. 2, the oil pumping member 12 includes an oil pumping portion 121 and a mounting portion 122, the oil pumping portion 121 is fitted in the central hole 111, a gap is provided between an outer circumferential wall of the oil pumping portion 121 and an inner circumferential wall of the central hole 111, a lower end surface of the oil pumping portion 121 is flush with a lower end surface of the crankshaft 11, the mounting portion 122 is connected to a lower end of the oil pumping portion 121, and the mounting portion 122 is provided with a mounting lug connected to the housing 5 of the compressor 100. This ensures both the pumping effect of the oil pump element 12 and the connection between the oil pump element 12 and the housing 5 of the compressor 100. It should be additionally noted that the mounting portion 122 may be fixed to the casing 5 of the compressor 100 by a wire, or may be connected to the casing 5 by a connecting rod, etc., and the connection form between the mounting portion 122 and the casing 5 is not specifically limited herein.
Example (b):
a compressor 100 according to one embodiment of the present application is described below with reference to fig. 1-5.
As shown in fig. 1, the compressor 100 of the present embodiment includes an oil supply structure 1, a frame 2, a stator 3, a rotor 4, and a casing 5.
The oil supply structure 1 comprises a crankshaft 11 and an oil pump part 12, the crankshaft 11 is vertically arranged, the crankshaft 11 is provided with a central hole 111, the oil pump part 12 is matched at the lower part of the central hole 111, a gap is formed between the outer peripheral wall of the oil pump part 12 and the inner peripheral wall of the central hole 111, and the oil pump part 12 can rotate relative to the crankshaft 11. The gap width between the outer peripheral wall of the oil pumping element 12 and the inner peripheral wall of the center hole 111 is S, which satisfies the relation: s is more than or equal to 0.04mm and less than or equal to 0.2 mm. The outer peripheral wall of the oil pump member 12 is provided with a spiral oil groove 1211 extending in a vertical spiral. The spiral oil groove 1211 has a width a and a depth b, and a and b satisfy the relationship: a is more than or equal to 1mm, and b is less than or equal to 1.5mm. The spiral oil groove 1211 has an axial length L, which satisfies the relationship: l is less than or equal to 50 mm. The number of lines of the spiral oil groove 1211 is 3. The spiral angle of the spiral oil groove 1211 is c, and c satisfies the relation: c is more than or equal to 15 degrees. The oil pump element 12 is provided with a vertically penetrating lightening hole 1212, and the lower end of the lightening hole 1212 is formed as a necking 1213. The crankshaft 11 has an outer diameter D1, the central bore 111 has a diameter D2, and D1 and D2 satisfy the relationship: d1 is less than or equal to 15mm, and D2 is more than or equal to 5mm. The frame 2 is provided with a shaft hole 21, the crankshaft 11 is arranged in the shaft hole 21 in a penetrating way, and the stator 3 and the rotor 4 are respectively arranged on the frame 2 and the crankshaft 11 and keep concentric. The lower end of the crankshaft 11 projects into the oil sump 6, which may be lower.
The oil pumping element 12 includes an oil pumping portion 121 and a mounting portion 122, the oil pumping portion 121 is fitted in the central hole 111, a gap is provided between an outer peripheral wall of the oil pumping portion 121 and an inner peripheral wall of the central hole 111, a lower end surface of the oil pumping portion 121 is flush with a lower end surface of the crankshaft 11, the mounting portion 122 is connected to a lower end of the oil pumping portion 121, and the mounting portion 122 is provided with a mounting lug connected to the housing 5 of the compressor 100.
In the compressor 100 of the present embodiment, the oil is supplied to a certain height through the spiral viscous oil supply structure 1, and then the lubricating oil is delivered to other parts of the compressor 100 through the oil supply hole above the crankshaft 11. The oil supply height of the spiral viscous oil supply structure 1 of the present embodiment is linear with the diameter of the crankshaft 11, and the oil supply height is much larger than the centrifugal oil pumping structure in the prior art, so that the compressor 100 of the present embodiment can provide sufficient lubricating oil for the refrigeration compressor 100 under the condition that the shaft diameter of the crankshaft 11 is thinned, and the efficiency and reliability of the compressor 100 are improved.
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 (8)
1. An oil supply structure for a compressor, comprising:
the crankshaft is vertically arranged and is provided with a central hole;
the oil pump piece is matched with the lower part of the central hole, a gap is formed between the outer peripheral wall of the oil pump piece and the inner peripheral wall of the central hole, the oil pump piece can rotate relative to the crankshaft, the oil pump height of the oil pump piece is in a linear relation with the diameter of the crankshaft, and an axially extending spiral oil groove is formed in the outer peripheral wall of the oil pump piece; the oil pump part is provided with a lightening hole which is through along the axial direction, and the lower end of the lightening hole is formed into a necking;
the outer diameter of the crankshaft is D1, the diameter of the central hole is D2, and D1 and D2 satisfy the relation: d1 is not more than 15mm, D2 is not less than 5mm, and the outer diameter D1 of the crankshaft and the diameter D2 of the central hole meet the relation: 2/3 is not less than D2/D1 is not less than 4/5.
2. The oil supply structure for a compressor according to claim 1, wherein a gap width between an outer peripheral wall of the oil pumping member and an inner peripheral wall of the center hole is S, S satisfying a relation: s is more than or equal to 0.04mm and less than or equal to 0.2 mm.
3. The oil supply structure for a compressor according to claim 2, wherein the spiral oil groove has a width a and a depth b, and a and b satisfy the relation: a is more than or equal to 1mm, and b is less than or equal to 1.5mm.
4. The oil supply structure for a compressor according to claim 2, wherein the helical oil groove has an axial length L satisfying a relation: l is less than or equal to 50 mm.
5. The oil supply structure for a compressor according to claim 2, wherein the number of the spiral oil groove lines is n, and n is a positive integer of 3 or less.
6. The oil supply structure for a compressor as claimed in claim 2, wherein a helix angle of the helical oil groove is c, and c satisfies a relation: c is more than or equal to 15 degrees.
7. A compressor, characterized by comprising the oil supply structure for a compressor according to any one of claims 1 to 6.
8. The compressor of claim 7, wherein the oil pumping member comprises:
the oil pumping part is matched in the central hole, a gap is formed between the outer peripheral wall of the oil pumping part and the inner peripheral wall of the central hole, and the lower end surface of the oil pumping part is flush with the lower end surface of the crankshaft;
the installation department, the installation department is connected the lower extreme of pump oil portion, the installation department be provided with the installation ear that the casing of compressor links to each other.
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| CN201811480168.1A CN111271254B (en) | 2018-12-05 | 2018-12-05 | Oil supply structure for compressor and compressor with same |
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| CN201811480168.1A CN111271254B (en) | 2018-12-05 | 2018-12-05 | Oil supply structure for compressor and compressor with same |
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| CN112032042A (en) * | 2020-08-31 | 2020-12-04 | 珠海格力节能环保制冷技术研究中心有限公司 | Oil pumping assembly, compressor and air conditioning unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003028065A (en) * | 2001-07-16 | 2003-01-29 | Matsushita Refrig Co Ltd | Hermetically closed electric compressor |
| CN106837745A (en) * | 2017-02-17 | 2017-06-13 | 安徽美芝制冷设备有限公司 | Compressor |
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| CN111271254A (en) | 2020-06-12 |
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