CN114198312A - Crankshaft oil guide assembly and compressor - Google Patents

Abstract

The invention provides a crankshaft oil guide assembly and a compressor, wherein the crankshaft oil guide assembly comprises a crankshaft and a rotary vane; the inside of bent axle has along the axial oil channel that leads that link up the setting, the rotor blade along the axial set up in lead in the oil channel, the bent axle has first end along radial, and first end has first depressed part, the one end of rotor blade has along the first bellying of radial setting, first bellying is used for the block to go into first depressed part, in order to restrict the rotor blade for the circumference degree of freedom of bent axle. The invention has the advantages of low processing requirement, high qualification rate and high installation precision, and can solve the problems that special processing equipment and professional installation personnel are required in the prior art, the qualification rate is low, and the installation precision cannot be ensured.

Description

Crankshaft oil guide assembly and compressor

Technical Field

The invention relates to the field of compressors, in particular to a crankshaft oil guide assembly and a compressor.

Background

In the existing refrigeration compressor, no matter the reciprocating piston compressor, the rotary piston compressor or the scroll compressor, the centrifugal oiling mode of installing the spiral rotary vane at the central oil hole of the crankshaft has more advantages than the oil pump oiling mode, and is the current mainstream structure. Along with the expansion of the rotary compressor to different fields, the displacement range of the rotary compressor is larger and larger, the lubricating environment of the rotary compressor with large displacement is worse, and the requirement on the lubrication of pump oil is higher and higher. Mainly focus on two aspects, firstly, after the installation, need to guarantee higher installation accuracy, and secondly, in the installation, hope its processing simply again, qualification rate is high.

The centrifugal oiling structure adopted by the industry at present adopts interference fit, and has the problems of low qualification rate and incapability of ensuring the installation precision due to the fact that special processing equipment and professional installation personnel are needed.

Disclosure of Invention

The invention aims to provide a crankshaft oil guide assembly and a compressor, and aims to solve the problem that the installation precision cannot be ensured as a special processing device and a professional installer are required for a conventional centrifugal oiling structure.

In order to solve the technical problem, the invention provides a crankshaft oil guide assembly, which comprises a crankshaft and a rotary vane; the inside of bent axle has along the axial oil channel that leads that link up the setting, the rotor blade along the axial set up in lead in the oil channel, the bent axle has first end along radial, and first end has first depressed part, the one end of rotor blade has along the first bellying of radial setting, first bellying is used for the block to go into first depressed part, in order to restrict the rotor blade for the circumference degree of freedom of bent axle.

Optionally, the crankshaft has a base surface that passes through a central axis of the oil guide passage and the first recess; the side wall of the crankshaft is provided with at least one oil outlet communicated with the oil guide channel; the base surface and at least one oil outlet hole satisfy the following relation:

tan(θ-εH)≥0

and theta is an angle formed by the oil outlet hole and the base plane along the rotation direction of the rotor plate, epsilon is the curvature of the rotor plate, and H is the axial distance between the same oil outlet hole and the first end.

Optionally, the side wall of the crankshaft is provided with more than two oil outlet holes, and each oil outlet hole meets the following requirements: tan (theta-epsilon H) is more than or equal to 0.

Optionally, the crankshaft includes an end cover disposed at the first end for limiting an axial degree of freedom of the rotor toward the first end.

Optionally, the end cover includes more than two jack catchs, the jack catch set up in the end cover is close to the one end of bent axle, and follows the circumference of end cover distributes, the end cover passes through the jack catch with lead oil passageway interference fit.

Optionally, the first recess is disposed at an end of the end cover close to the crankshaft.

Optionally, a second recess is formed in a side wall of the oil guide channel, a second protrusion is formed at one end, close to the crankshaft, of the end cover, and the second protrusion is used for being clamped into the second recess to limit circumferential freedom of the end cover relative to the crankshaft.

Optionally, the first recess is disposed on a sidewall of the oil guide passage.

Optionally, the first recess and the first protrusion are both trapezoidal in axial cross section along the oil guide channel, and the shorter base of the trapezoid is far away from the first end.

In order to solve the technical problem, the invention further provides a compressor, which comprises the crankshaft oil guide assembly and an oil storage cavity, wherein the first end is arranged in the oil storage cavity.

Compared with the prior art, the crankshaft oil guide assembly and the compressor provided by the invention comprise a crankshaft and a rotary vane; the crankshaft is provided with a first concave part, one end of the rotary vane is provided with a first convex part, and the first convex part is used for being clamped into the first concave part so as to limit the circumferential freedom degree of the rotary vane relative to the crankshaft. According to the scheme, the scheme that the interference fit mode is used for limiting the circumferential freedom degree of the rotary vane relative to the crankshaft is replaced, and the problem that the installation precision cannot be guaranteed due to the fact that a current centrifugal oiling structure needs special processing equipment and professional installation personnel is solved.

Drawings

It will be appreciated by those skilled in the art that the drawings are provided for a better understanding of the invention and do not constitute any limitation to the scope of the invention. Wherein:

FIG. 1 is a front view of a crankshaft according to a first embodiment of the present invention;

FIG. 2 is a cross-sectional view of a crankshaft oil guide assembly according to a first embodiment of the present invention;

FIG. 3a is a schematic view of the angle θ according to the first embodiment of the present invention;

FIG. 3b is another diagram of the angle θ according to the first embodiment of the present invention;

FIG. 4 is a schematic view of an end of a rotor plate with a first protrusion according to a second embodiment of the present invention;

FIG. 5 is a schematic cross-sectional view of a first recess according to a second embodiment of the present invention;

FIG. 6 is a schematic view of a crankshaft of a third embodiment of the present invention;

FIG. 7 is a schematic view of an end cap according to a third embodiment of the present invention;

fig. 8 is a front view of a crankshaft oil guide assembly and a crankshaft according to a third embodiment of the present invention.

In the drawings:

10-a crankshaft; 20-spinning; 30-a base surface; 40-end cap;

11-oil guide channel; 12-a first end; 13-a first recess; 14-oil outlet holes; 15-a second recess; 21-a first boss; 41-claws; 42-second boss.

Detailed Description

To further clarify the objects, advantages and features of the present invention, a more particular description of the invention will be rendered by reference to specific embodiments thereof which are illustrated in the appended drawings. It is to be noted that the drawings are in greatly simplified form and are not to scale, but are merely intended to facilitate and clarify the explanation of the embodiments of the present invention. Further, the structures illustrated in the drawings are often part of actual structures. In particular, the drawings may have different emphasis points and may sometimes be scaled differently.

As used in this application, the singular forms "a", "an" and "the" include plural referents, the term "or" is generally employed in a sense including "and/or," the terms "a" and "an" are generally employed in a sense including "at least one," the terms "at least two" are generally employed in a sense including "two or more," and the terms "first", "second" and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicit to the number of technical features indicated. Thus, features defined as "first", "second" and "third" may explicitly or implicitly include one or at least two of the features, "one end" and "the other end" and "proximal end" and "distal end" generally refer to the corresponding two parts, which include not only the end points, but also the terms "mounted", "connected" and "connected" should be understood broadly, e.g., as a fixed connection, as a detachable connection, or as an integral part; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. Furthermore, as used in the present invention, the disposition of an element with another element generally only means that there is a connection, coupling, fit or driving relationship between the two elements, and the connection, coupling, fit or driving relationship between the two elements may be direct or indirect through intermediate elements, and cannot be understood as indicating or implying any spatial positional relationship between the two elements, i.e., an element may be in any orientation inside, outside, above, below or to one side of another element, unless the content clearly indicates otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

The core idea of the invention is to provide a crankshaft oil guide assembly and a compressor, so as to solve the problems that the existing centrifugal oiling structure needs special processing equipment and professional installation personnel, the yield is low, and the installation precision cannot be ensured.

The following description refers to the accompanying drawings.

[ EXAMPLES one ]

Referring to fig. 1 to 3b, fig. 1 is a front view of a crankshaft according to a first embodiment of the present invention; FIG. 2 is a cross-sectional view of a crankshaft oil guide assembly according to a first embodiment of the present invention; FIG. 3a is a schematic view of the angle θ according to the first embodiment of the present invention; fig. 3b is another schematic diagram of the θ angle according to the first embodiment of the invention.

Fig. 1 and 2 show a crankshaft oil guide assembly including a crankshaft 10 and a rotor plate 20; the crankshaft 10 is internally provided with an oil guide channel 11 which is arranged in a penetrating manner along the axial direction, the rotor plate 20 is arranged in the oil guide channel 11 along the axial direction, the crankshaft 10 is provided with a first end 12 along the radial direction, the first end 12 is provided with a first concave part 13, one end of the rotor plate 20 is provided with a first convex part 21 which is arranged along the radial direction, and the first convex part 21 is used for being clamped into the first concave part 13 so as to limit the circumferential freedom degree of the rotor plate 20 relative to the crankshaft 10.

It is to be understood that the viewing direction of fig. 1 is from the exterior of the first end 12 toward the first end 12. Fig. 2 is a sectional view taken along a position where the base surface 30 shown in fig. 1 is located, and fig. 2 does not show an outer contour structure of the crankshaft for the sake of convenience of description, and a person skilled in the art can understand and arrange an outer structure of the crankshaft in the prior art, and a detailed description is not given here.

So configured, the cooperation mode of the rotary vane 20 and the oil guide channel 11 is replaced by the limit assembly from the interference fit, and a plurality of benefits are obtained. Firstly, the interference fit has higher processing precision requirements on the width of the rotary vane 20 and the inner diameter of the oil guide channel 11, and if the width of the rotary vane 20 is too wide or the inner diameter of the oil guide channel 11 is too narrow, the problem that the rotary vane and the oil guide channel cannot be assembled can occur; on the contrary, the binding force between the two is too small, and the whole mechanism is easy to loose during working, so that the whole mechanism fails. By adopting the scheme in the embodiment, the relation between the width of the rotary vane 20 and the inner diameter of the oil guide channel 11 is changed into clearance fit, and the requirement on machining precision is reduced. Secondly, the interference fit also has high requirements on assembly personnel, and the rotary vane 20 is a specially designed part and has high requirements on the shape and the size of the rotary vane during work. The interference fit often requires a large external force, so that the external force for assembly may affect the rotor plate 20 to cause large deformation, which affects the working performance, and in a more serious case, the rotor plate 20 may be broken, which causes waste of materials and time. In addition, if the coaxiality of the rotor plate 20 and the oil guide passage 11 is not ensured during the assembly process, the rotor plate 20 is also deformed due to the constraint force of the side wall of the oil guide passage 11 on the rotor plate, and the working performance is affected. From the current production practice, it is found that even if specially designed processing equipment is used to match with experienced assembly personnel, the final assembly result is not ideal and the lower rate is high. By adopting the scheme in the embodiment, the requirement on assembly personnel is hardly required, the required assembly force is small, and any specially designed processing equipment is not required. Finally, the existing compressor has high requirements on lubrication and oil output of the oil guide assembly, so that the relative position of the rotary vane 20 and the oil guide channel 11 is also high. In the interference fit process, the rotary plate 20 is difficult to fit to a better angle due to the lack of reference objects. By adopting the solution of the present embodiment, the first concave portion 13 can also be used as a reference standard for positioning, and as long as the first concave portion 13 is ensured to be in a better position when being processed, the finally assembled rotor plate 20 can be ensured to be in a better position. Compared with the prior art, the scheme shown in the embodiment has the advantages of low processing requirement, high qualification rate and high installation precision, and can solve the problems that special processing equipment and professional installation personnel are required in the prior art, the qualification rate is low, and the installation precision cannot be guaranteed.

In an exemplary embodiment, the crankshaft 10 has a base surface 30, the base surface 30 passing through a central axis of the oil guide passage 11 and the first recess 13; the side wall of the crankshaft 10 is provided with at least one oil outlet 14 communicated with the oil guide channel; the base surface 30 and at least one oil outlet hole 14 satisfy the following relationship:

tan(θ-εH)≥0

wherein θ is an angle formed by the oil outlet hole 14 and the base surface 30 along the rotation direction of the rotor plate 20, ε is a curvature of the rotor plate, and H is an axial distance between the same oil outlet hole 14 and the first end 12.

Theta is rotated in the rotation direction of the rotary plate 20, as can be understood in conjunction with fig. 3a and 3b, the viewing direction of fig. 3a and 3b being the same as that of fig. 1. In fig. 3a, the rotary vane 20 is right-handed (not shown), and the rotary direction of the rotary vane is counterclockwise when viewed from the viewing direction of fig. 3a, and the central axis of the oil outlet 14 starts to rotate counterclockwise until it meets the base surface 30, which is the angle θ. If the rotation direction of the rotary vane is clockwise when viewed from the opposite direction, the central axis of the oil outlet hole 14 also needs to be rotated clockwise until the base surface 30 is met. From the above description it is found that the direction of rotation for obtaining the angle θ is always the same as the direction of rotation of the rotor, whether the direction of observation chosen by the skilled person is the one of fig. 3a, or the opposite of fig. 3 a. Further, referring to fig. 3b, in fig. 3b, the rotary vane 20 is left-handed (not shown), and the rotation direction of the rotary vane is clockwise when viewed from the viewing direction of fig. 3b, and the central axis of the oil outlet 14 is rotated clockwise until the base 30 is encountered, and the angle through which the central axis passes is θ. If the rotation direction of the rotary vane is counterclockwise when viewed from the opposite direction, the central axis of the oil outlet hole 14 needs to be rotated counterclockwise until the base surface 30 is encountered. In summary, it can be concluded that the angle θ is the same as the rotation direction of the rotor 20 regardless of whether the rotor 20 is left-handed or right-handed, and whether the viewing direction is from the outside of the first end 12 toward the first end 12 or vice versa, and thus the reference standard for obtaining the angle θ can be set as the rotation direction of the rotor. In addition, the rotor curvature ε may be obtained by the following equation, which is an inherent property of rotor 20:

the rotor curvature epsilon is the total angle of rotation of the rotor/the length of the rotating part of the rotor.

The oil outlet 14 is provided in relation to the particular compressor configuration, and generally speaking, one oil outlet should be provided at each location where lubrication is required. Through experiments, the inventor finds that under the condition that other conditions are not changed, when the angle between the cross section of the rotary vane 20 at the oil outlet 14 and the oil outlet 14 is within 90 degrees, higher oil outlet amount can be ensured, and therefore better oil outlet effect can be ensured. And the angle can be obtained as follows:

step 1) calculation

Step 2) mixing

Plus or minus an integer number of 180 until it falls on 0, 180. In summary, in order to obtain a better oil-yielding effect, steps 1) and 2) can be performed first, and then:

step 3) order

By solving the equation, a preferable positioning dimension of the first recess 13 can be obtained.

Through observation, the steps 1), 2) and 3) can be combined and simplified to ensure that the tan (theta-epsilon H) is more than or equal to 0, so that better oil production effect can be obtained only by changing the positioning size of the first concave part 13 to ensure that the tan (theta-epsilon H) is more than or equal to 0.

Preferably, the side wall of the crankshaft is provided with more than two oil outlet holes 14, and each oil outlet hole 14 satisfies the following conditions: tan (theta-epsilon H) is more than or equal to 0.

When the positioning size of the first recess 13 is reasonably selected, the above criteria are established for each oil outlet 14, the parts corresponding to each oil outlet 14 can obtain a better lubricating effect, and therefore the compressor where the crankshaft oil guide assembly is located can obtain a better lubricating effect on the whole.

Preferably, referring to fig. 2, the crankshaft 10 includes an end cover 40, and the end cover 40 is disposed at the first end 12 for limiting the axial degree of freedom of the rotor 20 toward the first end.

Preferably, the end cover includes more than two claws 41, the claws 41 are arranged at one end of the end cover 40 close to the crankshaft 10 and distributed along the circumferential direction of the end cover 40, and the end cover 40 is in interference fit with the oil guide channel 11 through the claws 41.

With the above configuration, it is ensured that the end cover 40 is not axially displaced from the oil guide passage 11, and further, the end cover 40 restricts the axial degree of freedom of the rotor 20. Meanwhile, due to the existence of the clamping jaws 41, the follow-up maintenance and disassembly are facilitated.

With the above description, the main purpose of this embodiment is to replace the fitting manner of the rotary vane 20 and the oil guide channel 11 with the limit fitting from the interference fit by providing the first concave portion 13 and the first convex portion 21, and the present invention has the advantages of low processing requirement, high qualification rate and high installation accuracy, and can solve the problems that the prior art needs a special processing device and a professional installer, the qualification rate is low, and the installation accuracy cannot be guaranteed.

[ example two ]

Referring to fig. 4 and 5, fig. 4 is a schematic view of an end of a rotary plate having a first protrusion according to a second embodiment of the present invention; fig. 5 is a schematic cross-sectional view of a first recess according to a second embodiment of the present invention.

The embodiment provides a crankshaft oil guide assembly. In the present embodiment, the first recess 13 is disposed on a sidewall of the oil guide passage 11. The first concave part 13 and the first convex part 21 are both trapezoidal along the axial section of the oil guide channel 11, wherein the shorter base of the trapezoid is far away from the first end 12.

With such a configuration, the degree of freedom of the rotor 20 in the circumferential direction and the axial direction is more restricted, and the precision requirement for parts during machining can be further reduced.

[ EXAMPLE III ]

Referring to fig. 6 to 8, fig. 6 is a schematic view of a crankshaft according to a third embodiment of the present invention; FIG. 7 is a schematic view of an end cap according to a third embodiment of the present invention; fig. 8 is a front view of a crankshaft oil guide assembly and a crankshaft according to a third embodiment of the present invention.

The embodiment provides a crankshaft oil guide assembly. In the present embodiment, the first recess 13 is disposed at one end of the end cover 40 close to the crankshaft 10. The side wall of the oil guide channel 11 is provided with a second recess 15, one end of the end cover 40 close to the crankshaft 10 is provided with a second protrusion 42, and the second protrusion 42 is used for being clamped into the second recess 15 so as to limit the circumferential freedom degree of the end cover 40 relative to the crankshaft.

It is to be understood that in fig. 7, two claws 41 are provided as the second projecting portion 42, which is for saving the processing cost. However, the second projecting portion 42 may be a structure other than the claw 41.

Through the foregoing analysis, the relative position relationship between the first concave portion 13 and the crankshaft 10 has a better solution, but the better solution has a functional relationship with the rotor curvature ∈ of the rotor 20, that is, when the rotor curvature of the rotor 20 changes, the better solution also changes correspondingly, and if the better oil outlet effect is to be maintained continuously, the position size of the first concave portion 13 needs to change correspondingly. The following scenario is envisaged: in a compressor, in case that all the other parts are intact, the original vane 20 with the vane curvature of e 1 is damaged, and at this time, only the vane 20 with the vane curvature of e 2 is disposed in the factory, and if the first recess 13 is disposed on the sidewall of the oil guiding passage 11, if a superior oil discharging effect is to be maintained, the main body of the crankshaft 10 must be re-processed, and the maintenance cost is high.

In the present embodiment, the first recess 13 is provided above the end cap 40, which avoids the above-mentioned risk. On the premise of keeping a better oil outlet effect, if the curvature epsilon of the rotary vane 20 is changed, only a new end cover 40 with the positioning size of the first concave part 13 changed is replaced, the curvature epsilon of the new rotary vane can be matched, and the maintenance cost is low. In general, such a configuration decouples the intrinsic functional relationship between the dimensional parameters of the crankshaft 10 and the curvature epsilon of the rotor 20, and facilitates matching of the same crankshaft 10 with different rotors 20, thereby making the design more flexible and the maintenance cost lower.

[ EXAMPLE IV ]

The present embodiment provides a compressor, including a crankshaft oil guide assembly and an oil storage chamber, and details of the crankshaft oil guide assembly may refer to the first embodiment, the second embodiment, or the third embodiment. Wherein the first end is disposed in the oil storage cavity. At rest, the first end 12 of the crankshaft 10 is already filled with oil. When the crankshaft rotates, the engine oil moves upwards along the inclined plane formed by the rotary vane 20 and is thrown out of the oil guide channel 11 under the action of centrifugal force when meeting the oil outlet 14, so that the effect of lubricating other parts of the compressor is realized. The compressor also has the beneficial effects brought by the crankshaft oil guide assembly. Other parts and structures of the compressor can be arranged by those skilled in the art according to the actual prior art and will not be described in detail here.

It should be noted that, in the present specification, the embodiments are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments may be referred to each other. The above description is only for the purpose of describing the preferred embodiments of the present invention, and is not intended to limit the scope of the present invention, and any variations and modifications made by those skilled in the art based on the above disclosure are within the scope of the appended claims.

Claims (10)

1. The crankshaft oil guide assembly is characterized by comprising a crankshaft and a rotary vane; the inside of bent axle has along the axial oil channel that leads that link up the setting, the rotor blade along the axial set up in lead in the oil channel, the bent axle has first end along radial, and first end has first depressed part, the one end of rotor blade has along the first bellying of radial setting, first bellying is used for the block to go into first depressed part, in order to restrict the rotor blade for the circumference degree of freedom of bent axle.

2. The crankshaft oil guide assembly as claimed in claim 1, wherein the crankshaft has a base surface passing through a central axis of the oil guide passage and the first recess; the side wall of the crankshaft is provided with at least one oil outlet communicated with the oil guide channel; the base surface and at least one oil outlet hole satisfy the following relation:

tan(θ-εH)≥0

and theta is an angle formed by the oil outlet hole and the base plane along the rotation direction of the rotor plate, epsilon is the curvature of the rotor plate, and H is the axial distance between the same oil outlet hole and the first end.

3. The crankshaft oil guide assembly as claimed in claim 2, wherein the sidewall of the crankshaft has more than two oil outlet holes, and each oil outlet hole satisfies: tan (theta-epsilon H) is more than or equal to 0.

4. The crankshaft oil guide assembly as in claim 1, wherein said crankshaft comprises an end cap disposed at said first end for limiting an axial degree of freedom of said rotor toward said first end.

5. The crankshaft oil guide assembly according to claim 4, wherein the end cover comprises more than two claws, the claws are arranged at one end of the end cover close to the crankshaft and distributed along the circumferential direction of the end cover, and the end cover is in interference fit with the oil guide channel through the claws.

6. The crankshaft oil guide assembly as claimed in claim 4, wherein the first recess is disposed at an end of the end cover adjacent to the crankshaft.

7. The crankshaft oil guide assembly as in claim 6, wherein the side wall of the oil guide channel has a second recess, and the end cap has a second protrusion at an end near the crankshaft, the second protrusion being adapted to snap into the second recess to limit a circumferential degree of freedom of the end cap relative to the crankshaft.

8. The crankshaft oil guide assembly as claimed in claim 1, wherein the first recess is provided on a sidewall of the oil guide passage.

9. The crankshaft oil guide assembly as in claim 8, wherein the first concave portion and the first convex portion are both trapezoidal in axial cross section along the oil guide channel, and wherein the shorter base of the trapezoid is far from the first end.

10. A compressor comprising a crankshaft oil guide assembly as claimed in any one of claims 1 to 9 and an oil storage chamber, wherein the first end is disposed in the oil storage chamber.

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