CN111287967B - Rotary compressor - Google Patents

Rotary compressor Download PDF

Info

Publication number
CN111287967B
CN111287967B CN201811496822.8A CN201811496822A CN111287967B CN 111287967 B CN111287967 B CN 111287967B CN 201811496822 A CN201811496822 A CN 201811496822A CN 111287967 B CN111287967 B CN 111287967B
Authority
CN
China
Prior art keywords
welding
main
peripheral surface
shell
rotary compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201811496822.8A
Other languages
Chinese (zh)
Other versions
CN111287967A (en
Inventor
潘雯
吕林波
郑礼成
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Guangdong Meizhi Precision Manufacturing Co Ltd
Original Assignee
Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Guangdong Meizhi Precision Manufacturing Co Ltd filed Critical Guangdong Meizhi Precision Manufacturing Co Ltd
Priority to CN201811496822.8A priority Critical patent/CN111287967B/en
Publication of CN111287967A publication Critical patent/CN111287967A/en
Application granted granted Critical
Publication of CN111287967B publication Critical patent/CN111287967B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • F04C2230/23—Manufacture essentially without removing material by permanently joining parts together
    • F04C2230/231—Manufacture essentially without removing material by permanently joining parts together by welding

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The invention provides a rotary compressor, which comprises a main shell, a lower shell and a pump body, wherein the lower shell is welded at the bottom of the main shell, the pump body comprises a cylinder, an upper bearing and a lower bearing, the pump body is provided with a welding peripheral surface matched with the inner wall of the main shell, a welding part is arranged on the welding peripheral surface, a plurality of welding points are arranged between the main shell and the welding part along the circumferential direction, the lower part of the welding part is inwards recessed in the radial direction to form a first recessed part, one end of the first recessed part is positioned at the lower edge of the welding part, and the other end of the first recessed part is positioned at the lower edge of the welding peripheral surface, so that a gap is formed between the part of the welding peripheral surface, which is positioned below the welding part, and the main shell. The first depressed part reserves sufficient space for main casing body lower part shrink deformation, and after the main casing body produced shrink deformation with lower casing welding, still can guarantee to weld the position that lies in the weld part below on global and main casing body and have the clearance like this, solved the main casing body because of the problem of the lower extreme welding deformation extrusion pump body.

Description

Rotary compressor
Technical Field
The invention relates to the technical field of compressors, in particular to a rotary compressor.
Background
As shown in fig. 1 and 2, the conventional rotary compressor includes a main housing 1 ', a lower housing 2 ' and a pump body, the lower housing 2 ' is welded to the bottom of the main housing 1 ', the pump body includes a cylinder 3 ', an upper bearing 4 ' and a lower bearing 5 ', the cylinder 3 ', the upper bearing 4 ' or the lower bearing 5 ' of the pump body is welded to the inner wall of the main housing 1 ', and a plurality of welding points 6 ' are formed between the main housing 1 ' and the pump body along a circumferential direction. As shown in fig. 3, research shows that after the lower casing 2 ' is welded to the main casing 1 ', the welding residual stress and the thermal stress F may cause the lower end surface of the main casing 1 ' to contract and deform, and because the pump body is closer to the lower end surface of the main casing 1 ', the main casing 1 ' contracts and deforms to generate a larger extrusion force to a portion below a welding point 6 ' on the pump body (i.e., the cylinder 3 ', the upper bearing 4 ', or the lower bearing 5 ' welded to the main casing 1 '), so that positions such as an inner circle of the cylinder 3 ', a vane groove, or a bearing finish grinding surface, etc. are deformed, which may increase friction power of the vane groove and the piston, thereby affecting the performance of the rotary compressor, and if the deformation is too large, the vane or the piston may be jammed, which may affect the reliability of the rotary compressor.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art.
Accordingly, an object of the present invention is to provide a rotary compressor.
In order to achieve the above object, an embodiment of the present invention provides a rotary compressor, including a main housing, a lower housing, and a pump body, where the lower housing is welded at the bottom of the main housing, the pump body includes a cylinder, an upper bearing, and a lower bearing, the pump body has a welding peripheral surface that is matched with an inner wall of the main housing, a welding portion is disposed on the welding peripheral surface, a plurality of welding spots are circumferentially disposed between the main housing and the welding portion, a lower portion of the welding portion is radially inwardly recessed to form a first recessed portion, one end of the first recessed portion is located at a lower edge of the welding portion, and the other end of the first recessed portion is located at the lower edge of the welding peripheral surface, so that a gap is formed between a portion of the welding peripheral surface that is located below the welding portion and the main housing.
This scheme sets up first depressed part in the below of weld part, reserve sufficient space for main casing body lower part shrink deformation, after main casing body and lower casing welding produced shrink deformation like this, still can guarantee to weld the position that lies in the weld part below on global and main casing body and have the clearance, the problem of the main casing body because of lower extreme welding deformation extrusion pump body has been solved in this design, can improve the cylinder internal diameter, the problem that the sliding vane groove warp and the bearing finish grinding face warp because of main casing body extrusion, thereby can promote rotary compressor performance and reliability.
In the above technical solution, a point is arbitrarily selected on the first recess, a horizontal distance between the point and the welding portion is δ, and an inner diameter of the main housing is D1The thickness of the main shell is t1The thickness of the lower shell is t2The vertical distance between the center of the welding spot and the lower end face of the main shell is L1The vertical distance between the center of the welding spot and the point is L2The main housingAnd the tensile modulus of inferior valve body material is E, the main casing with the poisson's ratio of inferior valve body material is mu, the main casing with the yield strength of inferior valve body material is sigmasThen δ satisfies the following equation:
Figure GDA0003200657220000021
wherein:
Figure GDA0003200657220000022
the horizontal distance between the point on the first concave part and the welding part is the concave depth of the position, when the concave depth delta satisfies the relational expression, the concave depth of the first concave part is larger than the radial shrinkage of the welding deformation of the main shell body at the corresponding position, and therefore after the main shell body and the lower shell body are welded, the position below the welding part on the welding peripheral surface can still be ensured to have a gap with the main shell body.
In any one of the above technical solutions, preferably, a second recessed portion is formed by radially inwardly recessing above the welding portion, one end of the second recessed portion is located at an upper edge of the welding portion, and the other end of the second recessed portion is located at an upper edge of the welding peripheral surface, so that a gap is formed between a portion of the welding peripheral surface located above the welding portion and the main housing.
The top of main casing body need weld the casing, therefore main casing body up end also can produce shrinkage deformation because of the welding, though the pump body is usually far away from main casing body upper end, the position that lies in the welding portion top on the welding global still can receive main casing body and certain the extrusion. Therefore, the second concave part is arranged above the welding part, and enough space is reserved for the upper part of the main shell to shrink and deform, so that after the main shell is shrunk and deformed due to welding with the upper shell, the position above the welding part on the welding peripheral surface can be ensured to have a gap with the main shell, the problems of the inner diameter of the cylinder, the deformation of the sliding sheet groove and the deformation of the bearing finish grinding surface due to the extrusion of the main shell can be further improved, and the performance and the reliability of the rotary compressor can be further improved.
Specifically, the upper concave portion may be the same in shape and concave depth as the lower concave portion, or may be different from the lower concave portion. .
In any of the above technical solutions, preferably, a horizontal distance between each concave portion and the welding portion gradually increases from one end close to the welding point to one end far away from the welding point.
The shrinkage deformation volume of the main casing body is gradually increased from the welding position with the pump body to the end face, so that the concave depth of the concave part is gradually increased from one end close to the welding point to one end away from the welding point, the reserved avoiding space is close to the deformation volume of the main casing body, and thus, when the problem that the main casing body extrudes the pump body is improved, an overlarge gap is prevented from occurring between the peripheral surfaces of the main casing body and the pump body, and the problem that the pump body and the main casing body are not aligned is prevented from occurring.
In one embodiment of the present invention, each of the recesses is a bevel-avoiding groove or a fillet-avoiding groove extending from an edge of the welding portion to an edge of the welding periphery.
This scheme sets the depressed part to oblique angle or fillet structure for the horizontal distance of depressed part and weld part is crescent by the one end of being close to the solder joint to the one end of keeping away from the solder joint.
In another embodiment of the invention, each recess is a right-angle avoidance groove extending from the edge of the weld to the edge of the weld perimeter.
In another embodiment of the present invention, the first/second recess is a stepped groove extending from an edge of the welding part to an edge of the welding periphery.
This scheme sets the depressed part to the ladder groove structure for the horizontal distance of depressed part and weld part is increased step by step to the one end of keeping away from the solder joint by the one end that is close to the solder joint.
In any of the above technical solutions, an outer peripheral surface of the cylinder is the welded peripheral surface, or an outer peripheral surface of the upper bearing is the welded peripheral surface, or an outer peripheral surface of the lower bearing is the welded peripheral surface.
In any of the above technical solutions, one or more of the pump bodies are disposed in the main housing. Namely, the design is suitable for single-cylinder rotary compressors, double-cylinder rotary compressors and even multi-cylinder rotary compressors with more cylinders.
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 rotary compressor according to an embodiment of the prior art;
fig. 2 is a schematic structural view of a rotary compressor according to another embodiment of the prior art;
fig. 3 is a schematic view of a contracted and deformed pump body at the lower end of the main housing shown in fig. 1.
Wherein, the correspondence between the reference numbers and the component names in fig. 1 to 3 is:
1 'main shell, 2' lower shell, 3 'cylinder, 4' upper bearing, 5 'lower bearing, 6' welding point.
Fig. 4 is a schematic structural view of a rotary compressor according to a first embodiment of the present invention;
fig. 5 is a schematic structural view of the rotary compressor shown in fig. 4 after the main casing is shrunk and deformed;
fig. 6 is a schematic structural view of a rotary compressor according to a second embodiment of the present invention;
fig. 7 is a schematic structural view of a rotary compressor according to a third embodiment of the present invention;
fig. 8 is a schematic structural view of a rotary compressor according to a fourth embodiment of the present invention.
Wherein, the correspondence between the reference numbers and the part names in fig. 4 to 8 is:
the bearing comprises a main shell 1, a lower shell 2, a cylinder 3, an upper bearing 4, a lower bearing 5, a welding point 6, a first concave part 7 and a second concave part 8.
Detailed Description
In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced otherwise than as specifically described herein, and thus the scope of the present invention is not limited by the specific embodiments disclosed below.
The embodiment of the invention provides a rotary compressor, which comprises a main shell, a lower shell and a pump body, wherein the pump body comprises a cylinder, an upper bearing and a lower bearing, the pump body is provided with a welding peripheral surface matched with the inner wall of the main shell, a welding part is arranged on the welding peripheral surface, a plurality of welding points are arranged between the main shell and the welding part along the circumferential direction, the lower part of the welding part is inwards recessed in the radial direction to form a first recessed part, one end of the first recessed part is positioned at the lower edge of the welding part, and the other end of the first recessed part is positioned at the lower edge of the welding peripheral surface, so that a gap is formed between the part of the welding peripheral surface, which is positioned below the welding part, and the main shell.
A rotary compressor according to some embodiments of the present invention will be described with reference to fig. 4 to 8.
The first embodiment is as follows:
as shown in fig. 4 and 5, the rotary compressor includes a main housing 1, a lower housing 2, and a pump body, the lower housing 2 is welded to the bottom of the main housing 1, and the pump body includes a cylinder 3, an upper bearing 4, and a lower bearing 5. The outer peripheral surface of the cylinder 3 is a welding peripheral surface, the welding peripheral surface is provided with a welding part, the welding part is provided with a plurality of welding holes distributed in the circumferential direction, the main shell 1 corresponding to the welding part is also provided with small holes distributed in the same quantity, the cylinder 3 and the shell are welded and fixed by means of welding materials, the corresponding welding holes are filled in a plug welding mode, as shown in figure 6, one welding point is formed, and other welding points are not shown. The upper shell and the lower shell 2 are respectively fixed with the main shell 1 by girth welding of a butt joint after butt joint assembly, thereby forming a closed cavity of the rotary compressor. The lower part of the welding part of the cylinder 3 is inwards recessed in the radial direction to form a first recessed part 7, one end of the first recessed part 7 is positioned on the lower edge of the welding part, and the other end of the first recessed part 7 is positioned on the lower edge of the welding peripheral surface, so that a gap is formed between the part, below the welding part, of the welding peripheral surface and the main shell 1.
This scheme sets up first depressed part 7 in the below of weld part, reserve sufficient space for main casing body 1 lower part shrink deformation, after main casing body 1 produces shrink deformation with lower casing body 2 welding like this, still can guarantee that the position that lies in weld part below on the welding global has the clearance with main casing body 1, this design has solved main casing body 1 because of the problem of the lower extreme welding deformation extrusion pump body, can improve cylinder 3 internal diameter, the problem that the sliding vane groove warp and the bearing finish grinding face warp because of main casing body 1 extrusion, thereby can promote rotary compressor performance and reliability
Here, a horizontal distance δ from a welding portion to any point on the first recessed portion 7 is defined as follows: assuming that there is an initial gap delta between the main casing 1 and the cylinder 3 before girth welding0(not shown) main housing 1 has an inner diameter D1Thickness t1The thickness of the lower case 2 is t2The thickness of the lower case 2 is t2The vertical distance between the center of the welding point 6 and the lower end surface of the main shell 1 is L1The perpendicular distance between the center of the welding point 6 and the point is L2The main shell 1 and the lower shell 2 are made of the same material, and have the tensile modulus E, the Poisson ratio mu and the yield strength sigmas. Referring to fig. 4 and 5, a dot position is taken as an example at an end of the first recess 7 away from the welding point 6.
According to the theory of the elastic mechanics of the shell, in the section of the cylinder subjected to a load P uniformly distributed in the circumferential direction, the radial displacement it produces:
Figure GDA0003200657220000061
wherein:
Figure GDA0003200657220000062
the girth welding of the main case 1 and the lower case 2 can be approximately regarded as a weld seam welded at one time with a linear heat source, and the profitability after welding can be regarded as a one-way stress state in the direction of the weld seam regardless of the time effect of the welding process. The stress and deformation of the weld zone are caused byThe actual distribution of the residual strain of the weld, caused by plastic deformation in the weld zone, is reduced to equivalent strain which is uniformly distributed in the weld zone, and for general structural steel, the initial strain can be approximated to its yield strength. The circumferential butt weld of the cylinder only generates radial shrinkage deformation approximately, which can be equivalent to an even radial pressure P acting on the weld area in the circumferential direction, so that:
Figure GDA0003200657220000063
the deformation of the welding seam between the main shell 1 and the lower shell 2 can be regarded as being composed of two parts, the first part is a flat head sealing model formed by welding a thin plate cylinder in one single pass, and the head sealing part is a rigid fixed end, namely the deformation is regarded as being caused by the influence of welding residual stress, the elastic deformation of the lower shell 2 is not considered, and the column shell theory of the elastic mechanics is satisfied at the moment.
The second part is to take into account that the lower case 2 is elastically deformed by the welding force. According to a calculation formula of the mechanics of materials about the annular load, the method comprises the following steps:
Figure GDA0003200657220000064
due to t2＜＜D1Omit t2The second order square term of (a) is small, the above equation can be simplified to:
Figure GDA0003200657220000065
the deformation at the weld of the main case 1 and the lower case 2 is the sum of the two deformations: delta1＝δ′+δ″。
The main housing 1 at the lower end face of the cylinder 3 is then radially deformed into:
Figure GDA0003200657220000066
in order to ensure that the inner wall surface of the main shell 1 does not generate extrusion force on the cylinder 3 after the main shell 1 and the lower shell 2 are welded, the part below the welding part of the cylinder 3 is required to be ensured not to contact with the main shell 1,the maximum initial radial clearance δ of the side wall surfaces of the main housing 1 and the cylinder 3 then satisfies the following equation: delta>δ2。
Then, as can be seen from the above analysis, in order to ensure that the portion below the welding portion of the cylinder 3 does not contact the main casing 1, the horizontal distance δ from the welding portion to the end of the first recessed portion 7 away from the welding point 6 needs to satisfy the following formula:
Figure GDA0003200657220000071
wherein:
Figure GDA0003200657220000072
the horizontal distance between the first concave part 7 and the welding part is the concave depth of the position, when the concave depth delta satisfies the relational expression, the concave depth of the first concave part 7 is larger than the radial shrinkage of the welding deformation of the main casing body 1 at the corresponding position, so that after the main casing body 1 and the lower casing body 2 are welded, the position below the welding part on the welding peripheral surface can still be ensured to have a gap with the main casing body 1.
In the above embodiment, the first concave portion 7 is an oblique angle avoiding groove or a fillet avoiding groove extending from the edge of the welding portion to the lower edge of the cylinder 3, so that the horizontal distance between the first concave portion 7 and the welding portion gradually increases from the end close to the welding point 6 to the end away from the welding point 6. The shrinkage deformation volume of main casing body 1 is by gradually crescent with pump body splice to terminal surface, this scheme makes the sunken degree of depth of depressed part increase gradually from the one end that is close to solder joint 6 to the one end of keeping away from solder joint 6 for this reason, make the dodge space of reserving close to main casing body 1 deformation volume, can be improving when main casing body 1 extrudees the pump body problem like this, avoid main casing body 1 and the peripheral too big clearance of appearing of pump body welding, in order to prevent the pump body and the problem of main casing body 1 misalignment, avoid influencing rotary compressor's reliability and noise because of the pump body misalignment.
In the structure of the rotary compressor, the stator is fixed in the main shell 1 at the upper area of the main shell 1, and the local rigidity of the upper area of the main shell 1 is very large, so that the shrinkage deformation of the upper part of the main shell 1 is relatively small after welding residual stress and thermal stress, and the extrusion effect of the main shell 1 on the upper area of the side wall surface of the cylinder 3 is small after the welding residual stress and the thermal stress are applied to the main shell 1. For this reason, the upper area of the side wall surface of the cylinder 3 is not provided with a depressed part, so that the matching length of the minimum assembly clearance between the cylinder 3 and the main casing body 1 can be effectively increased, and the concentricity of the pump body and the main casing body 1 is ensured. Therefore, the embodiment not only gives consideration to the welding extrusion force of the main shell 1 to the pump body, but also ensures the concentricity of the pump body and the main shell 1 during the assembly of the rotary compressor, and is a better scheme.
Example two:
as shown in fig. 6, the design of the present embodiment is substantially the same as the first embodiment, except that a first concave portion 7 is provided below the welding portion of the cylinder 3, a second concave portion 8 which is concave radially inward is provided above the welding portion, one end of the second concave portion 8 is located at the upper edge of the welding portion, and the other end of the second concave portion 8 is located at the upper edge of the welding circumferential surface, so that the portion of the welding circumferential surface above the welding portion has a gap with the main housing 1.
Under the influence of the welding residual stress and the thermal stress of main casing body 1 and last casing, main casing body 1 top also can shrink deformation, cause certain extrusion to the pump body, for this scheme sets up second depressed part 8 in the top of weld part, reserve sufficient space for main casing body 1 upper portion shrink deformation, after main casing body 1 because of with last casing welding shrink deformation like this, still can guarantee to weld the position that lies in the weld part top on global and main casing body 1 and have the clearance, can further improve the 3 internal diameters of cylinder, the problem that the fine grinding face of sliding vane groove deformation and bearing warp because of main casing body 1 extrusion, thereby can further promote rotary compressor performance and reliability.
Wherein, the second depressed part 8 dodges the groove or the fillet dodges the groove for the oblique angle that extends to the last border of cylinder 3 by the border of weld part for the horizontal distance of second depressed part 8 and weld part is by being close to the one end of solder joint 6 to keeping away from the one end of solder joint 6 and increase gradually.
Specifically, the upper concave portion may be the same in shape and concave depth as the lower concave portion, or may be different from the lower concave portion.
Example three:
fig. 7 shows that the design of the present embodiment is substantially the same as the first embodiment, except that the first recess 7 is a right-angle avoiding groove extending from the edge of the welded portion to the lower edge of the cylinder 3 in the present embodiment.
Example four:
fig. 8 shows that the design of the present embodiment is substantially the same as that of the second embodiment, except that the first recessed portion 7 and the second recessed portion 8 are both right-angle avoiding grooves extending from the edge of the welded portion to the end surface of the cylinder 3 in this embodiment.
In any of the above embodiments, one or more pump bodies are provided within the main housing. Namely, the design is suitable for single-cylinder rotary compressors, double-cylinder rotary compressors and even multi-cylinder rotary compressors with more cylinders.
It should be noted that, in the above embodiments, the cylinder is welded to the main housing, that is, the outer peripheral surface of the cylinder is a welded peripheral surface, it is easy to think that the solutions of the embodiments may be replaced by welding the upper bearing or the lower bearing to the main housing, that is, the outer peripheral surface of the upper bearing or the lower bearing is a welded peripheral surface, and the welding points and the recessed portions are provided on the outer peripheral surface of the upper bearing or the lower bearing, so that these solutions should be included in the protection scope of the present invention.
In the description herein, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means 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.
In the description of the present invention, the terms "first," "second," "third," "fourth," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance, unless explicitly stated or limited otherwise; the terms "connected," "mounted," "secured," and the like are to be construed broadly and include, for example, fixed connections, removable connections, or integral connections; may be directly connected or indirectly connected through an intermediate. 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 above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (8)

1. A rotary compressor comprises a main shell, a lower shell and a pump body, wherein the lower shell is welded at the bottom of the main shell, the pump body comprises a cylinder, an upper bearing and a lower bearing, the pump body is provided with a welding peripheral surface matched with the inner wall of the main shell, the welding peripheral surface is provided with a welding part, a plurality of welding spots are arranged between the main shell and the welding part along the circumferential direction, the rotary compressor is characterized in that,
the welding part is characterized in that the lower part of the welding part is inwards recessed in the radial direction to form a first recessed part, one end of the first recessed part is located on the lower edge of the welding part, the other end of the first recessed part is located on the lower edge of the circumferential surface of the welding part, so that a gap is formed between the part, below the welding part, of the circumferential surface of the welding part and the main shell, a point is selected at will on the first recessed part, the horizontal distance between the point and the welding part is delta, and the inner diameter of the main shell is D1The thickness of the main shell is t1The thickness of the lower shell is t2The vertical distance between the center of the welding spot and the lower end face of the main shell is L1The vertical distance between the center of the welding spot and the point is L2The main casing with the tensile modulus of inferior valve body material is E, the main casing with the poisson's ratio of inferior valve body material is mu, the main casing with the yield strength of inferior valve body material is sigmasThen δ satisfies the following equation:
Figure FDA0003200657210000011
wherein:
Figure FDA0003200657210000012
2. the rotary compressor of claim 1,
the upper portion of the welding portion is radially inwards recessed to form a second recessed portion, one end of the second recessed portion is located on the upper edge of the welding portion, and the other end of the second recessed portion is located on the upper edge of the welding peripheral face, so that a gap is formed between the portion, located above the welding portion, of the welding peripheral face and the main shell.
3. The rotary compressor of claim 1 or 2,
the horizontal distance between each concave part and the welding part is gradually increased from one end close to the welding point to one end far away from the welding point.
4. The rotary compressor of claim 1 or 2,
each depressed part is by the border of welding part extends to the groove is dodged to the oblique angle at the border of welding periphery or the fillet groove is dodged.
5. The rotary compressor of claim 1 or 2,
each depressed part is by the border of welding portion extends to the right angle of the border of welding periphery dodges the groove.
6. The rotary compressor of claim 1 or 2,
each depressed part is a stepped groove extending from the edge of the welding part to the edge of the welding periphery.
7. The rotary compressor of claim 1 or 2,
the outer peripheral surface of the cylinder is the welding peripheral surface, or the outer peripheral surface of the upper bearing is the welding peripheral surface, or the outer peripheral surface of the lower bearing is the welding peripheral surface.
8. The rotary compressor of claim 1 or 2,
one or more of the pump bodies are disposed within the main housing.
CN201811496822.8A 2018-12-07 2018-12-07 Rotary compressor Active CN111287967B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201811496822.8A CN111287967B (en) 2018-12-07 2018-12-07 Rotary compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201811496822.8A CN111287967B (en) 2018-12-07 2018-12-07 Rotary compressor

Publications (2)

Publication Number Publication Date
CN111287967A CN111287967A (en) 2020-06-16
CN111287967B true CN111287967B (en) 2021-12-07

Family

ID=71030559

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201811496822.8A Active CN111287967B (en) 2018-12-07 2018-12-07 Rotary compressor

Country Status (1)

Country Link
CN (1) CN111287967B (en)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1643080A3 (en) * 2004-09-29 2007-12-19 Sanyo Electric Co., Ltd. Compressor with hermetically sealed container
CN101395379A (en) * 2006-03-07 2009-03-25 大金工业株式会社 Method for producing compressor, and compressor
CN202579195U (en) * 2010-12-15 2012-12-05 大金工业株式会社 Rotary fluid machine
CN204312327U (en) * 2014-12-02 2015-05-06 广东美芝制冷设备有限公司 Rotary compressor
CN106326667A (en) * 2016-08-31 2017-01-11 中国石油集团川庆钻探工程有限公司长庆井下技术作业公司 Well completion packer slip section casing ultimate bearing capacity calculation model and method
CN206874486U (en) * 2017-05-27 2018-01-12 安徽美芝精密制造有限公司 Rotary compressor

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7108489B2 (en) * 2003-04-15 2006-09-19 Tecumseh Products Company Terminal block assembly for a hermetic compressor
JP4820204B2 (en) * 2006-04-24 2011-11-24 三菱電機株式会社 Hermetic compressor, manufacturing apparatus and manufacturing method thereof
JP2011144788A (en) * 2010-01-18 2011-07-28 Toyota Industries Corp Motor-driven compressor
US9353749B2 (en) * 2013-07-31 2016-05-31 Agilent Technologies, Inc. Axially compliant orbiting plate scroll and scroll pump comprising the same
CN105805014B (en) * 2016-03-10 2018-06-15 广东美芝制冷设备有限公司 Multi-cylinder rotation compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1643080A3 (en) * 2004-09-29 2007-12-19 Sanyo Electric Co., Ltd. Compressor with hermetically sealed container
CN101395379A (en) * 2006-03-07 2009-03-25 大金工业株式会社 Method for producing compressor, and compressor
CN202579195U (en) * 2010-12-15 2012-12-05 大金工业株式会社 Rotary fluid machine
CN204312327U (en) * 2014-12-02 2015-05-06 广东美芝制冷设备有限公司 Rotary compressor
CN106326667A (en) * 2016-08-31 2017-01-11 中国石油集团川庆钻探工程有限公司长庆井下技术作业公司 Well completion packer slip section casing ultimate bearing capacity calculation model and method
CN206874486U (en) * 2017-05-27 2018-01-12 安徽美芝精密制造有限公司 Rotary compressor

Also Published As

Publication number Publication date
CN111287967A (en) 2020-06-16

Similar Documents

Publication Publication Date Title
JP6640216B2 (en) piston
KR20080043300A (en) Piston for an internal combustion engine
JP2016511367A (en) Welded piston assembly
JP5152731B2 (en) Multilayer gasket
US8387585B2 (en) Piston of an internal combustion engine with an increased inclination of the box walls of the piston
JP2010209862A (en) Piston of internal combustion engine
US9243583B2 (en) Piston for an internal combustion engine
US8955488B2 (en) Piston for use in internal combustion engines
WO2021126943A1 (en) Profiled cylinder liner for bore distortion control
CN111287967B (en) Rotary compressor
JP2018525562A (en) Piston for internal combustion engine
JP6817374B2 (en) piston ring
US7975601B2 (en) Engine cylinder liner
KR101497178B1 (en) Pin boss and piston having the same, for an internal combustion engine
CN113806880A (en) Method for designing plug skirt molded line suitable for large-cylinder-matching clearance piston
US20180045137A1 (en) Internal combustion engine piston having cooling gallery structure and internal combustion engine
US11371610B2 (en) Flutter-suppression piston ring
WO2006003976A1 (en) Piston ring for internal combustion engine
CN113606140B (en) Roller assembly, pump body assembly and compressor
CN103052787A (en) Piston of internal combustion engine and manufacturing method of piston
KR20180004290A (en) Piston for an internal combustion engine, and production method therefor
CN107002742A (en) Connecting rod
JP2019152233A5 (en)
CN108412630B (en) Three-cylinder engine piston
US10495022B2 (en) Piston for an internal combustion engine

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant