CN104595190B - Compressing mechanism for compressor and compressor with compressing mechanism - Google Patents
Compressing mechanism for compressor and compressor with compressing mechanism Download PDFInfo
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- CN104595190B CN104595190B CN201510057915.0A CN201510057915A CN104595190B CN 104595190 B CN104595190 B CN 104595190B CN 201510057915 A CN201510057915 A CN 201510057915A CN 104595190 B CN104595190 B CN 104595190B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a compressing mechanism for a compressor and the compressor with the compressing mechanism. The compressing mechanism comprises a cylinder assembly and a bearing arranged on one axial end of the cylinder assembly, wherein the cylinder assembly comprises a cylinder in which a compressing chamber is arranged; the bearing comprises a shaft neck part, a flange part and multiple first reinforcing ribs; the flange part is arranged between the shaft neck part and the cylinder assembly; in the axial direction of the cylinder assembly, the flange part comprises a support part which is axially opposite to the cylinder assembly; each first reinforcing rib extends along inner and outer directions and is arranged on one side, far away from the cylinder assembly, of the support part; and the multiple first reinforcing ribs are spaced at the periphery of the support part. According to the compressing mechanism, the rigidity of the bearing can be effectively increased by arranging the multiple first reinforcing ribs on the support part, so that the stress of the bearing is uniformly distributed, the utilization rate of the bearing material is improved and the production cost of the bearing is reduced.
Description
Technical field
The present invention relates to compressor apparatus field, especially relate to a kind of compression mechanism for compressor and there is it
Compressor.
Background technology
Bearing in compressor typically have of both effect, be on the one hand be located at the axial two ends of cylinder with cylinder
Between limit compression chamber, be on the other hand for supporting role being played to bent axle, pointing out in correlation technique, bearing only has
Enough rigid guarantee compressors normal and efficiently operating it is ensured that pressure reduction between compression chamber and external shell cavity
Under effect, bearing will not produce excessive axial deformation and make compression mechanism stuck or cause excessive running resistance；And, bearing
Only there is enough rigidity and just can ensure that the pressure between bearing and cylinder end face is enough, it is to avoid compression chamber is empty with external shell
Leak between chamber；In addition, bearing only has enough rigidity just can ensure that under the effect of motor unbalanced magnetic pull, turn
Son will not produce excessive deformation and come in contact and produce abnormal sound with stator.However, pointing out in correlation technique, only by bearing
The rigidity of the thicker guarantee bearing of diameter of axle portion and the design of flat flange portion, but the stress due to bearing different parts
Widely different, thus when bearing is made very thick, will be relatively low for the stock utilization leading to bearing, relatively costly.
Content of the invention
It is contemplated that at least solving one of technical problem present in prior art.For this reason, the invention reside in proposing one
Plant the compression mechanism for compressor, the rigidity of described compression mechanism middle (center) bearing is good, stock utilization is high, low cost.
The present invention also proposes a kind of compressor with compression mechanism.
The compression mechanism for compressor according to a first aspect of the present invention, including：Cylinder assembly and be located at described cylinder
The bearing of assembly axial direction one end, described cylinder assembly includes cylinder, has compression chamber in described cylinder, and described bearing includes：Axle
Cervical region；Flange portion, described flange portion is located between described collar and described cylinder assembly, in the axial direction of described cylinder assembly
On, described flange portion includes the support axially opposing with described cylinder assembly；And multiple first reinforcement, each described
One reinforcement all extends and is located at along inward-outward direction the side away from described cylinder assembly of described support, and the plurality of first
Reinforcement opens distribution in the circumferentially-spaced of described support.
According to the present invention for compressor compression mechanism, permissible by multiple first reinforcements are arranged on support
Effectively improve the rigidity of bearing so that the stress distribution of bearing is more uniform, improve the stock utilization of bearing, reduce bearing
Production cost.
Specifically, described cylinder is formed with the vane slot radially extending along described cylinder, the plurality of first reinforcement
One of described first reinforcement diametrically opposed in described cylinder with described vane slot.
Specifically, big in the width of described first reinforcement being radially oppositely arranged with described vane slot of described cylinder
The width of each described first reinforcement of remaining in the plurality of first reinforcement.
Specifically, limit cavity between two often adjacent the first reinforcements, described cylinder radially with described
The depth of the described cavity of described first reinforcement both sides that vane slot is oppositely arranged is less than in the plurality of first reinforcement
The depth of the described cavity limiting between remaining described first reinforcement.
Specifically, described cylinder is formed with the suction hole being connected with described compression chamber, in the plurality of first reinforcement
At least one described first reinforcement be correspondingly arranged in the axial direction of described cylinder with described suction hole.
Specifically, described support has delivery valve seat, the two ends on described delivery valve seat length direction are provided with described
First reinforcement.
Further, described bearing further includes：Second reinforcement, described second reinforcement is located at described support
Side away from described cylinder assembly and circumferentially extending along described support.
Specifically, described second reinforcement includes inner circumferential reinforcement, described inner circumferential reinforcement be connected to described collar with
Between described support.
Specifically, along direction from inside to outside, the axial width of described inner circumferential reinforcement is gradually reduced.
Specifically, described second reinforcement includes transition reinforcement, and described transition reinforcement is connected to described inner circumferential and strengthens
Between the inner of the outer rim of muscle and described first reinforcement.
Specifically, described second reinforcement includes periphery reinforcement, and described periphery reinforcement is located at the outer of described support
Between the outer end of edge and described first reinforcement.
Specifically, the installing hole described periphery reinforcement being formed through.
Specifically, in described support radially, described installing hole and described first reinforcement are correspondingly arranged.
Specifically, in the axial direction of described cylinder assembly, the side end face away from described cylinder assembly of described installing hole
The side away from described cylinder assembly positioned at described first reinforcement.
Alternatively, described periphery reinforcement is formed with the installation base being directed away from that described cylinder assembly direction is protruded,
Described installing hole is formed on described installation base.
Alternatively, described periphery reinforcement is formed with towards the recessed installation deep gouge in described cylinder assembly direction, described
Installing hole is formed on described installation deep gouge.
Compressor according to a second aspect of the present invention, including the compressor for compressor according to a first aspect of the present invention
Structure.
According to the compressor of the present invention, by arranging the compression mechanism for compressor of above-mentioned first aspect, thus carrying
The high overall performance of compressor.
The additional aspect of the present invention and advantage will be set forth in part in the description, and partly will become from the following description
Obtain substantially, or recognized by the practice of the present invention.
Brief description
Fig. 1 is the schematic diagram of bearing according to an embodiment of the invention；
Fig. 2 is the schematic diagram of compression mechanism according to an embodiment of the invention；
Fig. 3 is the schematic diagram of compression mechanism in accordance with another embodiment of the present invention；
Fig. 4 is the schematic diagram of bearing in accordance with another embodiment of the present invention；
Fig. 5 is the schematic diagram according to further embodiment compression mechanism of the present invention.
Reference：
1000：Compression mechanism；
100：Bearing；
1：Collar；
2：Flange portion；21：Support；21a：First face；21b：Second face；22：Outer perimeter section；
3：First reinforcement；
4：Second reinforcement；41：Inner circumferential reinforcement；42：Periphery reinforcement；
43：Transition reinforcement；44：Installation base；
5：Installing hole；6：Delivery valve seat；7：Solder joint；
200：Cylinder；201：Compression chamber；202：Vane slot；203：Suction hole.
Specific embodiment
Embodiments of the invention are described below in detail, the example of described embodiment is shown in the drawings, wherein from start to finish
The element that same or similar label represents same or similar element or has same or like function.Below with reference to attached
The embodiment of figure description is exemplary it is intended to be used for explaining the present invention, and is not considered as limiting the invention.
Following disclosure provides many different embodiments or example for realizing the different structure of the present invention.For letter
Change disclosure of the invention, hereinafter the part and setting of specific examples is described.Certainly, they are only merely illustrative, and
Purpose does not lie in the restriction present invention.Additionally, the present invention can in different examples repeat reference numerals and/or letter.This heavy
It is for purposes of simplicity and clarity again, itself do not indicate the relation between discussed various embodiment and/or setting.This
Outward, the invention provides various specific technique and material example, but those of ordinary skill in the art can be appreciated that
The applicable property of other techniques and/or the use of other materials.
The compression mechanism for compressor of embodiment according to a first aspect of the present invention is described below with reference to Fig. 1-Fig. 5
1000.Specifically, compressor (not shown) can also include housing (not shown), motor (not shown) and bent axle (figure
Not shown), wherein, housing can be formed generally as columnar hermetic container, and motor and compression mechanism 1000 are each provided at housing
Interior, and it is spaced apart setting in the axial direction of the housing, wherein, motor can include rotor and stator, and one end of bent axle is solid with rotor
Fixed, the other end of bent axle runs through compression mechanism 1000, so, when motor work, can by rotor driving crank rotation with
Coolant in compression mechanism 1000 is compressed.
As depicted in figs. 1 and 2, the compression mechanism 1000 for compressor of embodiment according to a first aspect of the present invention, bag
Include：Cylinder assembly and the bearing 100 being located at cylinder assembly axial direction one end, cylinder assembly includes cylinder 200, has in cylinder 200
Compression chamber 201.Wherein, compressor can be single cylinder compressor or multicylinder compressor, when compressor is for single cylinder compressor, cylinder
Assembly only includes a cylinder 200, the axial two ends of cylinder 200 can be respectively equipped with a bearing 100 with cylinder 200 between
Limit compression chamber 201, when compressor is for multicylinder compressor, cylinder assembly can include multiple cylinders 200, often adjacent two
Can have a dividing plate, the axial two ends of multiple cylinders 200 can be respectively equipped with a bearing 100, position between individual cylinder 200
Two cylinders 200 in axle head pass through dividing plate respectively and bearing 100 limits compression chamber 201, and remaining cylinders 200 can pass through it
The dividing plate at axial two ends limits compression chamber 201.Only so that compressor is as single cylinder compressor as a example illustrate below, certainly, pressure
Contracting machine can also be multicylinder compressor.Certainly, the invention is not restricted to this, bearing 100 can also be only defined the axial direction of cylinder assembly
One end, now the other end of cylinder assembly other kinds of bearing can also be set.
Specifically, bearing 100 includes collar 1 and flange portion 2, and flange portion 2 is located between collar 1 and cylinder assembly.
With reference to Fig. 1, collar 1 can be formed as substantially cylinder barrel shaped, and flange portion 2 can be formed as substantially disc, and collar 1 is located at
The side away from cylinder 200 of flange portion 2, and can from flange portion 2 away from a side end face of cylinder 200 center direction
Direction away from cylinder 200 extends, during assembling, can by flange portion 2 and cylinder 200 pass through threaded fastener (for example screw or
Bolt) etc. be assembled together, bearing 100 is fixed on cylinder 200.
Wherein, in the axial direction of cylinder assembly, flange portion 2 includes the support 21 axially opposing with cylinder assembly, also
To say, on the datum level perpendicular to cylinder assembly central axis, flange portion 2 with cylinder 200 in the axial direction of cylinder assembly
Just to part be support 21.For example in the example of Fig. 2 and Fig. 3, projection size on datum level for the flange portion 2 is less than gas
Projection size on datum level for the cylinder component, the now all supports 21 of flange portion 2, such as in the example of Fig. 4 and Fig. 5,
Flange portion 2 is more than projection size on datum level for the cylinder assembly in the projection size on datum level, and due to flange portion 2 and gas
Cylinder component coaxially assembles, thus in flange portion 2 only with cylinder assembly up and down just to inner round portion be support 21, and flange
The outer perimeter section 22 in portion 2 is not just right up and down with cylinder assembly, therefore is not support 21.Here, it should be noted that direction
" upper and lower " as broad understanding, that is, should be understood to the direction along cylinder assembly axis.
In order to simplify following description, with reference to Fig. 1, support 21 is neighbouring with the cylinder assembly and side surface that coordinates
It is defined as the first face 21a of support 21, by support 21 side surface relative with the first face 21a, i.e. support 21
A side surface away from cylinder assembly is defined as the second face 21b of bearing-surface.
Specifically, with reference to Fig. 1, bearing 100 also includes multiple first reinforcements 3, and each first reinforcement 3 is each provided at supporting
The side away from cylinder assembly in portion 21, that is, each first reinforcement 3 be each provided on the second face 21b of support 21, for example often
Individual first reinforcement 3 can be formed by the direction extension that the second face 21b of support 21 is directed away from cylinder assembly, thus each
The height of the first reinforcement 3 exceeds the height of the second face 21b of its both sides that is to say, that each the first reinforcement 3 and the first face
The distance between 21a is more than the distance between second face 21b and the first face 21a of its both sides.
Further, each first reinforcement 3 extends along inward-outward direction, and for example each first reinforcement 3 can be along flange
Portion 2 radially extends that is to say, that the extension line of the first reinforcement 3 can be to overlap with flange portion 2 RADIAL and cross bearing
100 central axis, and multiple first reinforcement 3 opens distribution that is to say, that often adjacent two in the circumferentially-spaced of support 21
Individual first reinforcement 3 is in the circumferentially-spaced certain distance of flange portion 2.Here, it should be noted that " interior " can be understood as court
To the direction of bearing 100 central axis, its rightabout is defined as " outward ", that is, away from the direction of bearing 100 central axis.Its
In, the first reinforcement 3 one directly can cast machine-shaping with flange portion 2, collar 1, so that bearing 100 is easy to into
Type, volume production feasibility is high.Certainly, the invention is not restricted to this, each first reinforcement 3 can also be without prolonging along the radial direction of flange portion 2
Stretch.
Thus, the rigidity of bearing 100 can be effectively improved it is ensured that compressor exists by arranging multiple first reinforcements 3
During operating, bearing 100 is not likely to produce excessive axial deformation, so that it is guaranteed that compression mechanism 1000 trouble-free operation, and not
There is problem stuck or that running resistance is excessive, and due to being provided with after multiple first reinforcements 3, the rigidity foot of bearing 100
Enough height may insure that the pressure between bearing 100 and cylinder 200 end face is enough, thus avoid compression mechanism 1000 revealing
Problem, in addition, it also avoid in motor (as mentioned below) work process produce abnormal sound problem.
Compression mechanism 1000 for compressor according to embodiments of the present invention, can be had by multiple first reinforcements 3
Effect ground improves the rigidity of bearing 100 so that the stress distribution of bearing 100 is more uniform, thus in the situation using less material
Lower bearing 100 just can reach the rigidity of correlation technique middle (center) bearing, and then is effectively improved the stock utilization of bearing 100,
Reduce the holistic cost of bearing 100.In addition, bearing 100 is easy to process, easy to utilize.
Specifically, cylinder 200 is formed with the vane slot 202 radially extending along cylinder 200 and connects with compression chamber 201
Suction hole 203.With reference to Fig. 2, Fig. 3 and Fig. 5, cylinder 200 could be formed with the compression lumen pore axially penetrating through along it, compress lumen pore
For limiting compression chamber 201, vane slot 202 can be from the side wall of compression lumen pore along radially outward recessed, the gas of cylinder 200
Steam vent (not shown) and suction hole 203 are formed further with cylinder 200, suction hole 203 and steam vent are respectively communicated to press
Contracting chamber 201, and suction hole 203 and steam vent are respectively provided at both sides and the neighbouring setting with vane slot 202 of vane slot 202.
In one embodiment of the invention, with reference to Fig. 2, one of multiple first reinforcements 3 first reinforcement 3a with
Vane slot 202 is diametrically opposed cylinder 200.That is, with the central axis of cylinder 200 as initial point and slide plate
Groove 202 is separated by 180 ° of position, has a first reinforcement 3a on the second face 21b of corresponding bearing 100.In other words, exist
On datum level, the projection of the projection and vane slot 202 that there is a first reinforcement 3a is located at the same diameter projection of cylinder 200
On line, and it is located at the both sides of cylinder 200 central axis.
Here, it should be noted that for High-back-pressure rotary compressor, when the corner of bent axle is 0 °, compressing
The pressure in chamber 201 is minimum, and now the part relative with compression chamber 201 on bearing 100 is in compression chamber 201 and enclosure interior pressure reduction
Effect is lower deform maximum, and maximum distortion occur on bearing 100 with vane slot 202 region diametrically in, so, when
The position diametrically with vane slot 202 on bearing 100 arranges the first reinforcement 3a, can effectively improve bearing 100
Problem on deformation.
Preferably, with reference to Fig. 2, in the width of the first reinforcement 3a being radially oppositely arranged with vane slot 202 of cylinder 200
Degree D1 is more than the width of remaining each the first reinforcement 3 in multiple first reinforcements 3, is greater than adjacent thereto first and adds
The width D 2 of strong muscle 3.Thus, it is possible to improve the problem on deformation of bearing 100 weakness further.Further, often adjacent two
Cavity 2a is limited, in first reinforcement being radially oppositely arranged with vane slot 202 of cylinder 200 between individual first reinforcement 3
The depth of the cavity 2a of muscle 3a both sides is less than the cavity limit between remaining first reinforcement 3 in multiple first reinforcements 3
Depth.Thus, it is possible to ensure bearing 100 with vane slot 202 part diametrically thickness larger, rigidity is stronger, from
And further improve the problem on deformation of bearing 100 weakness, improve the operational reliability of compressor.
Specifically, at least one of multiple first reinforcements 3 first reinforcement 3 and suction hole 203 are in the axle of cylinder 200
It is correspondingly arranged upwards.With reference to Fig. 3, on datum level, the projection of suction hole 203 and at least one first reinforcement 3 (such as Fig. 3
Shown in the first reinforcement 3b) projection substantially overlap, thus, it is possible to improve the intensity in this region for the bearing 100, and then subtract
The leakage of little compression mechanism 1000.Here it is possible to be understood by, because cylinder 200 suction hole 203 is to bearing 100 local stiffness
There is weakening effect that is to say, that being that bearing 100 contacts pressure with cylinder 200 suction hole 203 to corresponding position on bearing 100
The minimum region of power, improves the rigidity at this region of bearing 100 and advantageously reduces because pressure reduction leads in compression chamber 201 and housing
Leakage problem.
In one embodiment of the invention, with reference to Fig. 4 and Fig. 5, cylinder assembly can pass through two of its axial two ends
At least one of bearing 100 (clutch shaft bearing and second bearing) is exhausted that is to say, that cylinder assembly can only pass through the
One bearing is exhausted, and cylinder assembly can also be only exhausted by second bearing, and cylinder assembly can also both pass through first
Bearing is exhausted, and is exhausted further through second bearing.When cylinder assembly is only exhausted by clutch shaft bearing, first axle
Hold with delivery valve seat 6, second bearing does not have delivery valve seat 6, when cylinder assembly is only exhausted by second bearing
When, second bearing has delivery valve seat 6, clutch shaft bearing does not have delivery valve seat 6, when cylinder assembly had both passed through clutch shaft bearing
It is exhausted, when being exhausted further through second bearing, clutch shaft bearing and second bearing all have delivery valve seat 6.
Alternatively, as depicted in figs. 1 and 2, when bearing 100 does not have degassing function, on bearing 100, there are no aerofluxuss
During valve seat 6, support 21 can have multiple (five for example shown in Fig. 1) first reinforcement 3, and multiple first reinforcement
Muscle 3 can be evenly spaced apart distribution in the circumference of bearing 100, and wherein, each first reinforcement 3 can be along bearing 100
Radially extend, so that the stress distribution of bearing 100 is more uniform.
Alternatively, as shown in Figure 4 and Figure 5, when bearing 100 has degassing function, on bearing 100, there is delivery valve seat
When 6, delivery valve seat 6 is formed on support 21, and is respectively arranged at two ends with one first reinforcement on delivery valve seat 6 length direction
Muscle 3c.Specifically, valve seat can by the second face 21b of bearing 100 towards cylinder assembly direction recessed form, delivery valve seat 6
Two ends in bearing 100 circumference are respectively provided with a first reinforcement 3c, such that it is able to effectively improve bearing 100 air bleeding valve
Rigidity at seat 6, improves the problem on deformation of delivery valve seat 6 it is ensured that aerofluxuss reliability at delivery valve seat 6.
Specifically, bearing 100 further includes：Second reinforcement 4, the second reinforcement 4 be located at support 21 away from gas
The side of cylinder component and circumferentially extending along support 21.For example in the example of Fig. 1 and Fig. 4, the second reinforcement 4 is located at supporting
On the second face 21b in portion 21, and the second reinforcement 4 can be directed away from the side of cylinder assembly from the second face 21b of support 21
To extension, the second reinforcement 4 is circumferentially extending along support 21, the such as second reinforcement 4 can be formed as with support 21 outside
The concentric circular arc in edge, annular or interruption annular.
Specifically, the second reinforcement 4 includes inner circumferential reinforcement 41, and inner circumferential reinforcement 41 is connected to collar 1 and support
Between 21, and inner circumferential reinforcement 41 can be protruded by the direction that the second face 21b is directed away from cylinder assembly and form.For example in Fig. 1
In the example of Fig. 4, inner circumferential reinforcement 41 can extend to the second face 21b of support 21 from collar 1, thus being connected to axle
It is preferable that along direction from inside to outside, the axial width of inner circumferential reinforcement 41 is gradually reduced between footpath portion and support 21,
That is, the cross section of inner circumferential reinforcement 41 is formed as triangle, in other words, inner circumferential reinforcement 41 can be understood as being arranged on
The chamfering of axle journal root.
Thus, it is possible to the axial direction change that bearing 100 produces under compression chamber 201 and housing differential pressure action can be significantly reduced
Shape, thus reducing the running resistance of bent axle, and prevents the stuck problem of work of compressor simultaneously.In addition, inner circumferential reinforcement 41
The ability of the unbalanced magnetic pull of opposing motor of compression mechanism 1000 can also be effectively improved, thus subtracting trochantinian radial direction
Deformation is in case fastening and rotor contact and the abnormal sound that produces, and reduces the radial deformation of compression mechanism 1000 simultaneously, thus
Avoid that compression mechanism 1000 radial deformation is excessive and the vibration problem brought.
In addition, with reference to Fig. 4 and Fig. 5, on datum level, the projected area of bearing 100 is more than the projected area of cylinder assembly,
At this point it is possible to welded using bearing 100 (for example passing through the solder joint 7 shown in Fig. 4) to housing by the way of by compression mechanism 1000
It is fixed on housing, but, when bearing 100 only relies on the fixing cylinder 200 of support 21, on bearing 100, setting inner circumferential adds
Strong muscle 41 and transition reinforcement 43 can effectively improve the integral rigidity of compression mechanism 1000, such that it is able to effectively improve pressure
The reliability of contracting machine, reduces the vibration noise of compressor.Wherein, " integral rigidity of compression mechanism 1000 " refers to compression mechanism
The ability of 1000 opposing unbalanced magnetic pulls.
Further, the second reinforcement 4 can also include transition reinforcement 43, and transition reinforcement 43 is connected to inner circumferential and strengthens
Between the inner of the outer rim of muscle 41 and the first reinforcement 3.See figures.1.and.2, the inner of transition reinforcement 43 and inner circumferential reinforcement
41 are connected, and the outer end of transition reinforcement 43 is connected with the inner of the first reinforcement 3, and transition reinforcement 43 can be by the second face
The direction protrusion that 21b is directed away from cylinder assembly forms, thus, transition reinforcement 43 can assist inner circumferential reinforcement 41 further
Improving the integral rigidity of compression mechanism 1000, thus improving the reliability of compressor, reducing vibration and the abnormal sound of compressor.
Yet further, as Figure 1-Figure 5, the second reinforcement 4 can also include periphery reinforcement 42, periphery reinforcement
Between the outer end of 42 outer rims being located at support 21 and the first reinforcement 3, thus periphery reinforcement 42 can improve support 21
The rigidity at edge, improves the overall performance of bearing 100 further.
Alternatively, the installing hole 5 periphery reinforcement 42 being formed through.See figures.1.and.2, cylinder assembly and bearing
100 can be fixed together by threaded fastener, now, bearing 100 is formed with multiple installing holes 5, and multiple installing hole 5
It is both formed on periphery reinforcement 42, multiple installing holes 5 can open distribution in the circumferentially-spaced of support 21, thus, it is possible to
Effectively improve the rigidity in region between installing hole 5, thus when using threaded fastener (such as screw) by bearing 100 and cylinder
After assembly links together, the contact pressure between bearing 100 and cylinder assembly has ensured, improves the connection of bearing 100
Reliability and sealing tightness, and then avoid the leakage problem leading to due to the pressure reduction between compression chamber 201 and housing.
Specifically, in support 21 radially, installing hole 5 and the first reinforcement 3 are correspondingly arranged.With reference to Fig. 1, installing hole
5 may be located at the intersection that the first reinforcement 3 and periphery are strengthened, such that it is able to improve the rigidity of installing hole 5 local further,
Further increase the connection reliability of threaded fastener, further improve the leakage problem between compression chamber 201 and housing.
In addition, bearing 100 can adopt casting technique machine-shaping, then it is machined out more just can expiring at periphery reinforcement 42
The required precision on sufficient installing hole 5 surface, thus reducing processing cost, improves processing effect.
Preferably, with reference to Fig. 1, in the axial direction of cylinder assembly, the side end face away from cylinder assembly of installing hole 5 is located at
The side away from cylinder assembly of the first reinforcement 3 that is to say, that the height of installing hole 5 is higher than the height of the first reinforcement 3,
In other words, the distance between the side end face away from cylinder assembly of installing hole 5 and the first face 21a are more than the first reinforcement 3
The distance between a side end face away from cylinder assembly and the first face 21a.Thus, further facilitate machining, reduction is processed into
This, improve processing effect.
Further, with reference to Fig. 3, periphery reinforcement 42 could be formed with the peace being directed away from cylinder assembly direction protrusion
Dress boss 44, for example, installation base 44 can be protruded by the direction that the second face 21b of bearing 100 is directed away from cylinder assembly, from
And, the height of installation base 44 is higher than the height of periphery reinforcement 42, in other words, installation base 44 away from the one of cylinder assembly
The distance between side end face and the first face 21a are more than the side end face away from cylinder assembly and first face of periphery reinforcement 42
The distance between 21a it is preferable that in the axial direction of cylinder assembly, the side end face position away from cylinder assembly of installation base 44
In the first reinforcement 3 the side away from cylinder assembly that is to say, that the height of installation base 44 is also above the first reinforcement 3
Height, in other words, the distance between the side end face away from cylinder assembly of installation base 44 and first face 21a are more than first
The distance between a side end face away from cylinder assembly of reinforcement 3 and the first face 21a, now, it is convex that installing hole 5 is formed at installation
On platform 44.
Or alternatively, periphery reinforcement 42 can also be formed with towards the recessed installation deep gouge in cylinder assembly direction,
For example, installing deep gouge can be recessed towards the direction of cylinder assembly by the second face 21b of bearing 100, thus, the height of deep gouge is installed
Degree, less than the height of periphery reinforcement 42, in other words, is installed the distance between diapire and first face 21a of deep gouge and is added less than periphery
The distance between a side end face away from cylinder assembly of strong muscle 42 and the first face 21a, now, it is heavy that installing hole 5 is formed at installation
On groove, thus after assembling threaded fastener, the head of threaded fastener can sink in installation deep gouge, thus optimizing compressor
The overall structure of structure 1000.
So, bearing 100 can equally adopt casting technique machine-shaping, then on the surface of installation base 44 or
Person is machined out on the surface installing deep gouge, thus further reducing machining area, reduces bearing 100
Processing cost and process time.Further, since only need machine bearing 100 on periphery reinforcement 42, installation base 44 or
Deep gouge is installed, thus during cast bearing 100, enough allowance need not be left, casts such that it is able to reduce bearing 100 further
The processing cost of part.
Here, it should be noted that the shape of cross section of the first reinforcement 3 and the second reinforcement 4 all can be according to reality
Require setting, preferably to meet actual requirement, the shape of cross section of the such as first reinforcement 3 and the second reinforcement 4 is all permissible
Be formed as rectangle, triangle, trapezoidal, cydariform etc., and periphery reinforcement 42 can be formed as according to the design needs of installing hole 5
The rib of variable cross-section.In addition, the first reinforcement 3 and the second reinforcement 4 projection of shape on datum level can also be according to reality
Border requires to be designed, preferably to meet actual requirement.
In other embodiments of the present invention, compression mechanism 1000 can also include deafener (not shown), noise reduction
Device can be fixed on the side away from cylinder assembly of the bearing 100 with delivery valve seat 6, is made an uproar with the aerofluxuss reducing compressor
Sound, due to limiting some grooves between the first reinforcement 3, the second reinforcement 4, thus work as assemble deafener with bearing 100
After putting in place, the silence space between deafener and bearing 100 can be improved, such that it is able to effectively improve erasure effect, improve
The sound-damping qualities of deafener and noise reduction frequency etc..
The compressor of embodiment according to a second aspect of the present invention, including the use according to the present invention above-mentioned first aspect embodiment
Compression mechanism 1000 in compressor.Wherein, compressor can be vertical compressor or horizontal compressor.
Compressor according to embodiments of the present invention, by arranging the compression for compressor of above-mentioned first aspect embodiment
Mechanism 1000, thus improve the overall performance of compressor.
In describing the invention it is to be understood that term " width ", " thickness ", " on ", D score, " top ", " bottom ",
The orientation of instruction such as " interior ", " outward ", " axial ", " radially ", " circumferential " or position relationship are based on orientation shown in the drawings or position
Put relation, be for only for ease of and describe the present invention and simplify description, rather than indicate or imply that the device of indication or element are necessary
There is specific orientation, with specific azimuth configuration and operation, be therefore not considered as limiting the invention.
Additionally, term " first ", " second " are only used for describing purpose, and it is not intended that indicating or hint relative importance
Or the implicit quantity indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can express or
Implicitly include one or more this feature.In describing the invention, " multiple " are meant that two or more,
Unless otherwise expressly limited specifically.
In the present invention, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection ", " fixation " etc.
Term should be interpreted broadly, for example, it may be being fixedly connected or being detachably connected or integral；It can be direct phase
Even it is also possible to be indirectly connected to by intermediary, can be the connection of two element internals or the interaction pass of two elements
System.For the ordinary skill in the art, above-mentioned term in the present invention concrete can be understood as the case may be
Implication.
In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score permissible
It is the first and second feature directly contacts, or the first and second features pass through intermediary mediate contact.And, fisrt feature exists
Second feature " on ", " top " and " above " but fisrt feature are directly over second feature or oblique upper, or be merely representative of
Fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " lower section " and " below " can be
One feature is immediately below second feature or obliquely downward, or is merely representative of fisrt feature level height and is less than second feature.
In the description of this specification, reference term " embodiment ", " some embodiments ", " example ", " specifically show
The description of example " or " some examples " etc. means specific features, structure, material or the spy describing with reference to this embodiment or example
Point is contained at least one embodiment or the example of the present invention.In this manual, to the schematic representation of above-mentioned term not
Identical embodiment or example must be directed to.And, the specific features of description, structure, material or feature can be in office
Combine in an appropriate manner in one or more embodiments or example.Additionally, in the case of not conflicting, the skill of this area
The feature of the different embodiments described in this specification or example and different embodiment or example can be tied by art personnel
Close and combine.
Although an embodiment of the present invention has been shown and described, it will be understood by those skilled in the art that：Not
Multiple changes, modification, replacement and modification can be carried out to these embodiments in the case of the principle of the disengaging present invention and objective, this
The scope of invention is limited by claim and its equivalent.
Claims (16)
1. a kind of compression mechanism for compressor is it is characterised in that include：Cylinder assembly and be located at described cylinder assembly axially
The bearing of one end, described cylinder assembly includes cylinder, has compression chamber in described cylinder, and described bearing includes：
Collar；
Flange portion, described flange portion is located between described collar and described cylinder assembly, in the axial direction of described cylinder assembly,
Described flange portion includes the support axially opposing with described cylinder assembly；And
Multiple first reinforcements, each described first reinforcement all along inward-outward direction extend and be located at described support away from institute
State the side of cylinder assembly, the plurality of first reinforcement opens distribution in the circumferentially-spaced of described support,
The vane slot radially extending along described cylinder is formed with described cylinder, one of the plurality of first reinforcement is described
First reinforcement is diametrically opposed in described cylinder with described vane slot.
2. the compression mechanism for compressor according to claim 1 it is characterised in that described cylinder radially with
The width of described first reinforcement that described vane slot is oppositely arranged is more than remaining each institute in the plurality of first reinforcement
State the width of the first reinforcement.
3. the compression mechanism for compressor according to claim 1 is it is characterised in that often adjacent two first are strengthened
Cavity is limited, in the described first reinforcement both sides being radially oppositely arranged with described vane slot of described cylinder between muscle
The depth of described cavity is less than the described sky limit between remaining described first reinforcement in the plurality of first reinforcement
The depth in chamber.
4. the compression mechanism for compressor according to claim 1 is it is characterised in that be formed with described cylinder and institute
State the suction hole of compression chamber connection, described first reinforcement of at least one of the plurality of first reinforcement and described suction hole
The axial direction of described cylinder is correspondingly arranged.
5. the compression mechanism for compressor according to claim 1 is it is characterised in that have aerofluxuss on described support
Valve seat, the two ends on described delivery valve seat length direction are provided with described first reinforcement.
6. the compression mechanism for compressor according to any one of claim 1-5 is it is characterised in that described bearing enters
One step includes：
Second reinforcement, described second reinforcement is located at the side away from described cylinder assembly of described support and along described
Bearing portion circumferentially extending.
7. the compression mechanism for compressor according to claim 6 is it is characterised in that in described second reinforcement includes
All reinforcements, described inner circumferential reinforcement is connected between described collar and described support.
8. the compression mechanism for compressor according to claim 7 is it is characterised in that along direction from inside to outside,
The axial width of described inner circumferential reinforcement is gradually reduced.
9. the compression mechanism for compressor according to claim 7 was it is characterised in that described second reinforcement included
Cross reinforcement, described transition reinforcement is connected between the outer rim of described inner circumferential reinforcement and the inner of described first reinforcement.
10. the compression mechanism for compressor according to claim 6 is it is characterised in that described second reinforcement includes
Periphery reinforcement, described periphery reinforcement is located between the outer rim of described support and the outer end of described first reinforcement.
11. compression mechanisms for compressor according to claim 10 are it is characterised in that shape on the reinforcement of described periphery
Become to have the installing hole running through.
12. compression mechanisms for compressor according to claim 11 are it is characterised in that radial direction in described support
On, described installing hole is correspondingly arranged with described first reinforcement.
13. compression mechanisms for compressor according to claim 11 are it is characterised in that axle in described cylinder assembly
Upwards, the side end face away from described cylinder assembly of described installing hole be located at described first reinforcement away from described air cylinder group
The side of part.
14. compression mechanisms for compressor according to claim 11 are it is characterised in that shape on the reinforcement of described periphery
Become and have the installation base being directed away from that described cylinder assembly direction is protruded, described installing hole is formed on described installation base.
15. compression mechanisms for compressor according to claim 11 are it is characterised in that shape on the reinforcement of described periphery
Become to have towards the recessed installation deep gouge in described cylinder assembly direction, described installing hole is formed on described installation deep gouge.
A kind of 16. compressors are it is characterised in that include the pressure for compressor according to any one of claim 1-15
Contracting mechanism.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510057915.0A CN104595190B (en) | 2015-02-04 | 2015-02-04 | Compressing mechanism for compressor and compressor with compressing mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510057915.0A CN104595190B (en) | 2015-02-04 | 2015-02-04 | Compressing mechanism for compressor and compressor with compressing mechanism |
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| CN104595190A CN104595190A (en) | 2015-05-06 |
| CN104595190B true CN104595190B (en) | 2017-02-22 |
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| CN201510057915.0A Active CN104595190B (en) | 2015-02-04 | 2015-02-04 | Compressing mechanism for compressor and compressor with compressing mechanism |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110439817A (en) * | 2019-09-12 | 2019-11-12 | 珠海凌达压缩机有限公司 | Cylinder, pump body subassembly and compressor suitable for compressor |
| CN112253462A (en) * | 2020-10-26 | 2021-01-22 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61255290A (en) * | 1985-05-07 | 1986-11-12 | Matsushita Electric Ind Co Ltd | Closed type rotary compressor |
| JP2862260B2 (en) * | 1989-03-16 | 1999-03-03 | 株式会社日立製作所 | Rotary compressor |
| CN1966986A (en) * | 2005-11-14 | 2007-05-23 | 乐金电子(天津)电器有限公司 | Upper bearing structure in rotary compressor |
| CN101684799A (en) * | 2008-09-27 | 2010-03-31 | 乐金电子(天津)电器有限公司 | Two-stage rotating type compressor |
| CN201412339Y (en) * | 2009-06-02 | 2010-02-24 | 沈阳华润三洋压缩机有限公司 | Bearing of reinforced structure |
| CN201513345U (en) * | 2009-10-13 | 2010-06-23 | 珠海格力电器股份有限公司 | Birotor two-stage enthalpy-increasing compressor, air conditioner and heat pump water heater |
| CN204436791U (en) * | 2015-02-04 | 2015-07-01 | 广东美芝制冷设备有限公司 | For compressor compressing mechanism and there is its compressor |
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