CN104595190A - 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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- CN104595190A CN104595190A CN201510057915.0A CN201510057915A CN104595190A CN 104595190 A CN104595190 A CN 104595190A CN 201510057915 A CN201510057915 A CN 201510057915A CN 104595190 A CN104595190 A CN 104595190A
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- stiffening rib
- cylinder assembly
- bearing
- compressing mechanism
- compressor according
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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
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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
- 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 compressing mechanism for compressor and there is its compressor.
Background technique
Bearing in compressor generally has the effect of two aspects, that the axial two ends being located at cylinder are to limit compression chamber between cylinder on the one hand, for playing supporting role to bent axle on the other hand, point out in correlation technique, bearing only has enough rigidity guarantee compressors normally and operate efficiently, under guaranteeing the differential pressure action between compression chamber and external casing cavity, the excessive axial deformation of the unlikely generation of bearing makes compressing mechanism stuck or cause excessive running resistance; And bearing only has enough rigidity just can guarantee that the pressure between bearing and cylinder end face is enough, avoids leaking between compression chamber and external casing cavity; In addition, bearing only has enough rigidity and just can guarantee that, under the effect of motor unbalanced magnetic pull, the distortion that the unlikely generation of rotor is excessive and stator come in contact and produce different sound.But, point out to only have the rigidity of the thicker guarantee bearing designed in the diameter of axle portion of bearing and flat flange part in correlation technique, but because the stress difference of bearing different parts is very large, thus when bearing does very thick, by causing, the stock utilization of bearing is lower, and cost is higher.
Summary of the invention
The present invention is intended at least to solve one of technical problem existed in prior art.For this reason, the invention reside in and propose a kind of compressing mechanism for compressor, the good rigidly of described compressing mechanism middle (center) bearing, stock utilization is high, cost is low.
The present invention also proposes a kind of compressor with compression mechanism.
The compressing mechanism for compressor according to a first aspect of the present invention, comprising: cylinder assembly and the bearing being located at the axial one end of described cylinder assembly, and described cylinder assembly comprises cylinder, has compression chamber in described cylinder, and described bearing comprises: collar; Flange part, described flange part is located between described collar and described cylinder assembly, and at described cylinder assembly axially, described flange part comprises the support axially relative with described cylinder assembly; And multiple first stiffening rib, each described first stiffening rib all extends along inward-outward direction and is located at the side away from described cylinder assembly of described support, the spaced apart distribution in the circumference of described support of described multiple first stiffening rib.
According to the compressing mechanism for compressor of the present invention, effectively can improve the rigidity of bearing by arranging multiple first stiffening rib on support, making the stress distribution of bearing more even, improving the stock utilization of bearing, reduce the cost of production of bearing.
Particularly, described cylinder is formed with the vane slot extended along described cylinder radial direction, described first stiffening rib in described multiple first stiffening rib and described vane slot are oppositely arranged in the radial direction of described cylinder.
Particularly, the width of described first stiffening rib radial direction of described cylinder is oppositely arranged with described vane slot is greater than the width of all the other each described first stiffening ribs in described multiple first stiffening rib.
Particularly, cavity is limited, in the radial direction of described cylinder and the degree of depth of the described cavity of described first stiffening rib both sides that is oppositely arranged of the described vane slot degree of depth of described cavity that is less than in described multiple first stiffening rib to limit between the first stiffening rib described in all the other between two often adjacent the first stiffening ribs.
Particularly, described cylinder is formed with the suction port be communicated with described compression chamber, described at least one in described multiple first stiffening rib, the first stiffening rib is arranged the axially corresponding of described cylinder with described suction port.
Particularly, described support has delivery valve seat, the two ends on described delivery valve seat length direction are provided with described first stiffening rib.
Further, described bearing comprises further: the second stiffening rib, and described second stiffening rib is located at the side away from described cylinder assembly of described support and the circumference along described support extends.
Particularly, described second stiffening rib comprises inner circumferential stiffening rib, and described inner circumferential stiffening rib is connected between described collar and described support.
Particularly, along direction from inside to outside, the axial thickness of described inner circumferential stiffening rib reduces gradually.
Particularly, described second stiffening rib comprises transition stiffening rib, and described transition stiffening rib is connected between the outer rim of described inner circumferential stiffening rib and the inner of described first stiffening rib.
Particularly, described second stiffening rib comprises periphery stiffening rib, and described periphery stiffening rib is located between the outer rim of described support and the outer end of described first stiffening rib.
Particularly, described periphery stiffening rib is formed with the mounting hole run through.
Particularly, in the radial direction of described support, described mounting hole is corresponding with described first stiffening rib to be arranged.
Particularly, at described cylinder assembly axially, the side end face away from described cylinder assembly of described mounting hole is positioned at the side away from described cylinder assembly of described first stiffening rib.
Alternatively, described periphery stiffening rib is formed towards the installation base protruded away from described cylinder assembly direction, described mounting hole is formed on described installation base.
Alternatively, described periphery stiffening rib is formed with the installation deep gouge recessed towards described cylinder assembly direction, described mounting hole is formed on described installation deep gouge.
Compressor according to a second aspect of the present invention, comprises the compressing mechanism for compressor according to a first aspect of the present invention.
According to compressor of the present invention, by arranging the compressing mechanism for compressor of above-mentioned first aspect, thus improve the overall performance of compressor.
Additional aspect of the present invention and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by practice of the present invention.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of bearing according to an embodiment of the invention;
Fig. 2 is the schematic diagram of compressing mechanism according to an embodiment of the invention;
Fig. 3 is the schematic diagram of compressing 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 another embodiment's compressing mechanism of the present invention.
Reference character:
1000: compressing mechanism;
100: bearing;
1: collar;
2: flange part; 21: support; 21a: first surface; 21b: the second; 22: outer perimeter section;
3: the first stiffening ribs;
4: the second stiffening ribs; 41: inner circumferential stiffening rib; 42: periphery stiffening rib;
43: transition stiffening rib; 44: installation base;
5: mounting hole; 6: delivery valve seat; 7: solder joint;
200: cylinder; 201: compression chamber; 202: vane slot; 203: suction port.
Embodiment
Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.
Disclosing hereafter provides many different embodiments or example is used for realizing different structure of the present invention.Of the present invention open in order to simplify, hereinafter the parts of specific examples and setting are described.Certainly, they are only example, and object does not lie in restriction the present invention.In addition, the present invention can in different example repeat reference numerals and/or letter.This repetition is to simplify and clearly object, itself does not indicate the relation between discussed various embodiment and/or setting.In addition, the various specific technique that the invention provides and the example of material, but those of ordinary skill in the art can recognize the property of can be applicable to of other techniques and/or the use of other materials.
The compressing mechanism 1000 for compressor of embodiment is according to a first aspect of the present invention described below with reference to Fig. 1-Fig. 5.Particularly, compressor (scheming not shown) can also comprise housing (scheming not shown), motor (scheming not shown) and bent axle (scheming not shown), wherein, housing can be formed as columnar seal container substantially, motor and compressing mechanism 1000 are all located in housing, and spaced apart setting in the axial direction of the housing, wherein, motor can comprise rotor and stator, one end and the rotor of bent axle are fixed, the other end of bent axle runs through compressing mechanism 1000, like this, when machine operation, can be rotated by rotor driving crank to compress the refrigerant in compressing mechanism 1000.
As depicted in figs. 1 and 2, the compressing mechanism 1000 for compressor of embodiment according to a first aspect of the present invention, comprising: cylinder assembly and the bearing 100 being located at the axial one end of cylinder assembly, cylinder assembly comprises cylinder 200, has compression chamber 201 in cylinder 200.Wherein, compressor can be single cylinder compressor or multicylinder compressor, when compressor is single cylinder compressor, cylinder assembly only comprises a cylinder 200, the axial two ends of cylinder 200 can be respectively equipped with a bearing 100 to limit compression chamber 201 between cylinder 200, when compressor is multicylinder compressor, cylinder assembly can comprise multiple cylinder 200, a dividing plate can be had between two often adjacent cylinders 200, the axial two ends of multiple cylinder 200 can be respectively equipped with a bearing 100, two cylinders 200 being positioned at axle head limit compression chamber 201 respectively by dividing plate and bearing 100, remaining cylinders 200 can limit compression chamber 201 by the dividing plate at its axial two ends.Be only single cylinder compressor below with compressor for example is described, certainly, compressor can also be multicylinder compressor.Certainly, the present invention is not limited thereto, bearing 100 only can also be located at axial one end of cylinder assembly, and now the other end of cylinder assembly can also arrange the bearing of other types.
Particularly, bearing 100 comprises collar 1 and flange part 2, and flange part 2 is located between collar 1 and cylinder assembly.With reference to Fig. 1, collar 1 can be formed as cylinder barrel shaped substantially, flange part 2 can be formed as disc substantially, collar 1 is located at the side away from cylinder 200 of flange part 2, and can extend from the center of the side end face away from cylinder 200 of flange part 2 towards the direction away from cylinder 200, during assembling, flange part 2 and cylinder 200 can be assembled together by threaded fastener (such as screw or bolt) etc., to be fixed on cylinder 200 by bearing 100.
Wherein, at cylinder assembly axially, flange part 2 comprises the support 21 axially relative with cylinder assembly, that is, on the reference level perpendicular to cylinder assembly central axis, flange part 2 be support 21 with cylinder 200 in the axially just right part of cylinder assembly.Such as in the example of Fig. 2 and Fig. 3, the projection size of flange part 2 on reference level is less than the projection size of cylinder assembly on reference level, now flange part 2 is all support 21, such as in the example of Fig. 4 and Fig. 5, the projection size of flange part 2 on reference level is greater than the projection size of cylinder assembly on reference level, and coaxially assemble due to flange part 2 and cylinder assembly, thus flange part 2 only has the inner round portion just right up and down with cylinder assembly be support 21, and the outer perimeter section 22 of flange part 2 is not just right up and down with cylinder assembly, therefore it not support 21.Here, it should be noted that, broad understanding is used as in direction " up and down ", namely should be understood to the direction along cylinder assembly axis.
In order to simplify following description, with reference to Fig. 1, by the contiguous with cylinder assembly of support 21 and the side surface definition coordinated is the first surface 21a of support 21, be second 21b of supporting surface by the side surface definition away from cylinder assembly of a side surface, the i.e. support 21 relative with first surface 21a of support 21.
Particularly, with reference to Fig. 1, bearing 100 also comprises multiple first stiffening rib 3, each first stiffening rib 3 is all located at the side away from cylinder assembly of support 21, namely each first stiffening rib 3 is all located on second 21b of support 21, such as each first stiffening rib 3 can be formed towards the direction extension away from cylinder assembly by second of support 21 21b, thus the height of each first stiffening rib 3 exceeds the height of second 21b of its both sides, that is, distance between each first stiffening rib 3 and first surface 21a is greater than the distance between second 21b of its both sides and first surface 21a.
Further, each first stiffening rib 3 extends along inward-outward direction, such as each first stiffening rib 3 can extend along the radial direction of flange part 2, that is, the line stretcher of the first stiffening rib 3 can be overlap with flange part 2 radial line and cross bearing 100 central axis, and the spaced apart distribution in the circumference of support 21 of multiple first stiffening rib 3, that is, two often adjacent the first stiffening ribs 3 keep at a certain distance away in the circumference of flange part 2.Here, it should be noted that, " interior " can be understood as the direction towards bearing 100 central axis, and its opposite direction is defined as " outward ", namely away from the direction of bearing 100 central axis.Wherein, the first stiffening rib 3 one directly can be cast machine shaping with flange part 2, collar 1, thus make bearing 100 be easy to shaping, and volume production feasibility is high.Certainly, the present invention is not limited thereto, each first stiffening rib 3 can not also extend along the radial direction of flange part 2.
Thus, the rigidity of bearing 100 effectively can be improved by arranging multiple first stiffening rib 3, guarantee that compressor is in the process of running, bearing 100 not easily produces excessive axial deformation, thus guarantee compressing mechanism 1000 trouble-free operation, and there is not stuck or that running resistance is excessive problem, and due to after being provided with multiple first stiffening rib 3, the rigidity of bearing 100 is enough high can guarantee that the pressure between bearing 100 and cylinder 200 end face is enough, thus avoid the problem that leakage occurs compressing mechanism 1000, in addition, it also avoid the different mail topic produced in motor (as mentioned below) working procedure.
According to the compressing mechanism 1000 for compressor of the embodiment of the present invention, the rigidity of bearing 100 effectively can be improved by multiple first stiffening rib 3, make the stress distribution of bearing 100 more even, thus the rigidity utilizing the situation lower bearing 100 of less material just can reach correlation technique middle (center) bearing, and then effectively improve the stock utilization of bearing 100, reduce the holistic cost of bearing 100.In addition, bearing 100 is easy to processing, easy to utilize.
Particularly, cylinder 200 is formed with the vane slot 202 extended along cylinder 200 radial direction and the suction port 203 be communicated with compression chamber 201.With reference to Fig. 2, Fig. 3 and Fig. 5, cylinder 200 can be formed with the compression lumen pore axially run through along it, compression lumen pore is used for limiting compression chamber 201, vane slot 202 can be recessed into from the sidewall of compression lumen pore along the radially outward of cylinder 200, cylinder 200 is formed with further exhaust port (scheming not shown) and suction port 203, suction port 203 and exhaust port are communicated to compression chamber 201 respectively, and suction port 203 and exhaust port are located at the both sides of vane slot 202 respectively and arrange with vane slot 202 is contiguous.
In one embodiment of the invention, with reference to Fig. 2, a first stiffening rib 3a in multiple first stiffening rib 3 and vane slot 202 are oppositely arranged in the radial direction of cylinder 200.That is, be initial point with the central axis of cylinder 200, second 21b of be separated by with vane slot 202 position of 180 °, corresponding bearing 100 has a first stiffening rib 3a.In other words, on reference level, there is the projection of a first stiffening rib 3a and the projection of vane slot 202 is positioned on the same diameter projection line of cylinder 200, and be positioned 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 °, the pressure of compression chamber 201 is minimum, the part relative with compression chamber 201 now on bearing 100 is out of shape maximum under compression chamber 201 with enclosure interior differential pressure action, and maximum distortion appear on bearing 100 with in vane slot 202 region diametrically, like this, when arranging the first stiffening rib 3a with vane slot 202 position diametrically on bearing 100, the problem on deformation of bearing 100 effectively can be improved.
Preferably, with reference to Fig. 2, the width D 1 of the first stiffening rib 3a that the radial direction of cylinder 200 is oppositely arranged with vane slot 202 is greater than the width of all the other each first stiffening ribs 3 in multiple first stiffening rib 3, such as, be greater than the width D 2 of the first stiffening rib 3 adjacent thereto.Thus, the problem on deformation of bearing 100 weakness can be improved further.Further, cavity 2a is limited, in the radial direction of cylinder 200 and the degree of depth of the cavity 2a of the first stiffening rib 3a both sides that is oppositely arranged of vane slot 202 degree of depth of cavity that is less than in multiple first stiffening rib 3 to limit between all the other first stiffening ribs 3 between two often adjacent the first stiffening ribs 3.Thus, can ensure the comparatively large with the thickness of vane slot 202 part diametrically of bearing 100, rigidity is comparatively strong, thus improves the problem on deformation of bearing 100 weakness further, improves the operational reliability of compressor.
Particularly, at least one first stiffening rib 3 in multiple first stiffening rib 3 is arranged the axially corresponding of cylinder 200 with suction port 203.With reference to Fig. 3, on reference level, the projection of suction port 203 overlaps substantially with the projection of at least one the first stiffening rib 3 (the first stiffening rib 3b such as shown in Fig. 3), thus, the intensity of bearing 100 in this region can be improved, and then reduce the leakage of compressing mechanism 1000.Here, be understandable that, because cylinder 200 suction port 203 pairs of bearing 100 local stiffness have weakening effect, that is, bearing 100 is the region that bearing 100 contact is minimum to corresponding position with cylinder 200 suction port 203, the rigidity improving this region place of bearing 100 is conducive to the leakage problem reduced because pressure reduction in compression chamber 201 and housing causes.
In one embodiment of the invention, with reference to Fig. 4 and Fig. 5, cylinder assembly can be exhausted by least one in two bearings 100 (clutch shaft bearing and the second bearing) at its axial two ends, that is, cylinder assembly can be exhausted by means of only clutch shaft bearing, cylinder assembly can also be exhausted by means of only the second bearing, and cylinder assembly can also be both exhausted by clutch shaft bearing, is exhausted again by the second bearing.When cylinder assembly is exhausted by means of only clutch shaft bearing, clutch shaft bearing has delivery valve seat 6, second bearing do not have delivery valve seat 6, when cylinder assembly is exhausted by means of only the second bearing, second bearing has delivery valve seat 6, clutch shaft bearing does not have delivery valve seat 6, when cylinder assembly was both exhausted by clutch shaft bearing, when being exhausted by the second bearing again, clutch shaft bearing and the second bearing all has delivery valve seat 6.
Alternatively, as depicted in figs. 1 and 2, when bearing 100 does not have degassing function, when namely bearing 100 not having delivery valve seat 6, support 21 can have multiple (five such as shown in Fig. 1) first stiffening rib 3, and multiple first stiffening rib 3 can be evenly spaced apart distribution in the circumference of bearing 100, wherein, each first stiffening rib 3 can extend along the radial direction of bearing 100, to make the stress distribution of bearing 100 more even.
Alternatively, as shown in Figure 4 and Figure 5, when bearing 100 has degassing function, when namely bearing 100 having delivery valve seat 6, delivery valve seat 6 is formed on support 21, and the two ends on delivery valve seat 6 length direction are respectively equipped with a first stiffening rib 3c.Particularly, valve seat can form by second of bearing 100 21b is recessed towards the direction of cylinder assembly, the two ends of delivery valve seat 6 in bearing 100 circumference have a first stiffening rib 3c respectively, thus effectively can improve the rigidity at bearing 100 delivery valve seat 6 place, improve the problem on deformation of delivery valve seat 6, guarantee the exhaust reliability at delivery valve seat 6 place.
Particularly, bearing 100 comprises further: the second stiffening rib 4, second stiffening rib 4 is located at the side away from cylinder assembly of support 21 and the circumference along support 21 extends.Such as in the example of Fig. 1 and Fig. 4, second stiffening rib 4 is located on second 21b of support 21, and the second stiffening rib 4 can extend from second of support 21 21b towards the direction away from cylinder assembly, second stiffening rib 4 extends along the circumference of support 21, and such as the second stiffening rib 4 can be formed as circular arc, the ring concentric with support 21 outward edge or be interrupted ring.
Particularly, the second stiffening rib 4 comprises inner circumferential stiffening rib 41, and inner circumferential stiffening rib 41 is connected between collar 1 and support 21, and inner circumferential stiffening rib 41 can be formed towards the direction protrusion away from cylinder assembly by second 21b.Such as in the example of Fig. 1 and Fig. 4, inner circumferential stiffening rib 41 can extend by second 21b from collar 1 to support 21, thus be connected between diameter of axle portion and support 21, preferably, along direction from inside to outside, the axial thickness of inner circumferential stiffening rib 41 reduces gradually, that is, the cross section of inner circumferential stiffening rib 41 is formed as triangle, and in other words, inner circumferential stiffening rib 41 can be understood as the chamfering being arranged on axle journal root.
Thus, the axial deformation that bearing 100 produces under compression chamber 201 and housing differential pressure action can be reduced significantly, thus reduce the running resistance of bent axle, and prevent the stuck problem of the work of compressor simultaneously.In addition, inner circumferential stiffening rib 41 can also improve the ability of the unbalanced magnetic pull of the opposing motor of compressing mechanism 1000 effectively, thus subtract trochantinian radial deformation in case fastening and rotor contact and the different sound that produces, and reduce the radial deformation of compressing mechanism 1000, thus avoid the excessive and vibration problem brought of compressing mechanism 1000 radial deformation simultaneously.
In addition, with reference to Fig. 4 and Fig. 5, on reference level, the area of contour of bearing 100 is greater than the area of contour of cylinder assembly, now, bearing 100 (such as by the solder joint 7 shown in Fig. 4) to the mode of housing of welding can be adopted to be fixed on housing by compressing mechanism 1000, but, when bearing 100 only relies on support 21 to fix on cylinder 200, bearing 100 arranges the integral rigidity that inner circumferential stiffening rib 41 and transition stiffening rib 43 can improve compressing mechanism 1000 effectively, thus effectively can improve the reliability of compressor, reduce the vibration noise of compressor.Wherein, " integral rigidity of compressing mechanism 1000 " refers to the ability that compressing mechanism 1000 resists unbalanced magnetic pull.
Further, the second stiffening rib 4 can also comprise transition stiffening rib 43, and transition stiffening rib 43 is connected between the outer rim of inner circumferential stiffening rib 41 and the inner of the first stiffening rib 3.See figures.1.and.2, the inner of transition stiffening rib 43 is connected with inner circumferential stiffening rib 41, the outer end of transition stiffening rib 43 is connected with the inner of the first stiffening rib 3, and transition stiffening rib 43 can be formed towards the direction protrusion away from cylinder assembly by second 21b, thus, transition stiffening rib 43 can assist inner circumferential stiffening rib 41 to improve the integral rigidity of compressing mechanism 1000 further, thus improves the reliability of compressor, reduces the vibration of compressor and different sound.
Again further, as Figure 1-Figure 5, second stiffening rib 4 can also comprise periphery stiffening rib 42, periphery stiffening rib 42 is located between the outer rim of support 21 and the outer end of the first stiffening rib 3, thus periphery stiffening rib 42 can improve the rigidity at support 21 edge, improve the overall performance of bearing 100 further.
Alternatively, periphery stiffening rib 42 is formed with the mounting hole 5 run 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 mounting hole 5, and multiple mounting hole 5 is all formed on periphery stiffening rib 42, multiple mounting hole 5 can spaced apart distribution in the circumference of support 21, thus, effectively can improve the rigidity in region between mounting hole 5, thus after bearing 100 and cylinder assembly link together by employing threaded fastener (such as screw), contact between bearing 100 and cylinder assembly ensures to some extent, improve connection reliability and the sealing leakproofness of bearing 100, and then avoid the leakage problem caused due to the pressure reduction between compression chamber 201 and housing.
Particularly, in the radial direction of support 21, mounting hole 5 is corresponding with the first stiffening rib 3 to be arranged.With reference to Fig. 1, mounting hole 5 can be positioned at the intersection of the first stiffening rib 3 and periphery Jia Qiang Zhu, thus the rigidity of mounting hole 5 local can be improved 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, and then carries out at periphery stiffening rib 42 place the required precision that machining just can meet mounting hole 5 surface, thus reduces processing cost, improves processing effect.
Preferably, with reference to Fig. 1, at cylinder assembly axially, a side end face away from cylinder assembly of mounting hole 5 is positioned at the side away from cylinder assembly of the first stiffening rib 3, that is, the height of mounting hole 5 is higher than the height of the first stiffening rib 3, and in other words, the distance between the side end face away from cylinder assembly of mounting hole 5 and first surface 21a is greater than the distance between the side end face away from cylinder assembly of the first stiffening rib 3 and first surface 21a.Thus, further facilitate machining, cut down finished cost, improve processing effect.
Further, with reference to Fig. 3, periphery stiffening rib 42 can be formed towards the installation base 44 protruded away from cylinder assembly direction, such as, installation base 44 can be protruded towards the direction away from cylinder assembly by second of bearing 100 21b, thus, the height of installation base 44 is higher than the height of periphery stiffening rib 42, in other words, distance between a side end face away from cylinder assembly of installation base 44 and first surface 21a is greater than the distance between the side end face away from cylinder assembly of periphery stiffening rib 42 and first surface 21a, preferably, at cylinder assembly axially, a side end face away from cylinder assembly of installation base 44 is positioned at the side away from cylinder assembly of the first stiffening rib 3, that is, the height of installation base 44 is also higher than the height of the first stiffening rib 3, in other words, distance between a side end face away from cylinder assembly of installation base 44 and first surface 21a is greater than the distance between the side end face away from cylinder assembly of the first stiffening rib 3 and first surface 21a, now, mounting hole 5 is formed on installation base 44.
Or alternatively, periphery stiffening rib 42 can also be formed with the installation deep gouge recessed towards cylinder assembly direction, such as, deep gouge is installed to be recessed into towards the direction of cylinder assembly by second of bearing 100 21b, thus, the height of height lower than periphery stiffening rib 42 of deep gouge is installed, in other words, the distance of installing between the diapire of deep gouge and first surface 21a is less than the distance between the side end face away from cylinder assembly of periphery stiffening rib 42 and first surface 21a, now, mounting hole 5 is formed in be installed on deep gouge, thus after assembling threaded fastener, the head of threaded fastener can sink to be installed in deep gouge, thus optimize the overall structure of compressing mechanism 1000.
Like this, bearing 100 can adopt the processes of casting shaping equally, then on the surface of installation base 44 or on the surface of installing deep gouge, carry out machining, thus further reduce machining area, reduce processing cost and the process time of bearing 100.In addition, owing to only needing the periphery stiffening rib 42 on machining bearing 100, installation base 44 or installing deep gouge, thus during cast bearing 100, without the need to leaving enough machining allowance, thus the processing cost of bearing 100 foundry goods can be reduced further.
Here, it should be noted that, the shape of cross section of the first stiffening rib 3 and the second stiffening rib 4 all can be arranged according to actual requirement, to meet actual requirement better, the such as shape of cross section of the first stiffening rib 3 and the second stiffening rib 4 all can be formed as rectangle, triangle, trapezoidal, cydariform etc., and periphery stiffening rib 42 according to the design needs of mounting hole 5, can be formed as the rib of variable cross-section.In addition, the first stiffening rib 3 and the projection of shape of the second stiffening rib 4 on reference level can also design according to actual requirement, to meet actual requirement better.
In other embodiments of the present invention, compressing mechanism 1000 can also comprise baffler (scheming not shown), baffler can be fixed on the side away from cylinder assembly of the bearing 100 with delivery valve seat 6, to reduce the exhaust noise of compressor, owing to limiting some grooves between the first stiffening rib 3, second stiffening rib 4, thus after baffler and bearing 100 are seated, the silence space between baffler and bearing 100 can be improved, thus effectively can improve erasure effect, improve the sound-damping qualities and noise reduction frequency etc. of baffler.
The compressor of embodiment according to a second aspect of the present invention, comprises the compressing mechanism 1000 for compressor according to the above-mentioned first aspect embodiment of the present invention.Wherein, compressor can be vertical compressor or horizontal compressor.
According to the compressor of the embodiment of the present invention, by arranging the compressing mechanism 1000 for compressor of above-mentioned first aspect embodiment, thus improve the overall performance of compressor.
In describing the invention, it will be appreciated that, term " width ", " thickness ", " on ", D score, " top ", " end ", " interior ", " outward ", " axis ", " radial direction ", the orientation of the instruction such as " circumference " or position relationship be based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore can not be interpreted as limitation of the present invention.
In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristics.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise one or more these features.In describing the invention, the implication of " multiple " is two or more, unless otherwise expressly limited specifically.
In the present invention, unless otherwise clearly defined and limited, the term such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements.For the ordinary skill in the art, above-mentioned term concrete meaning in the present invention can be understood as the case may be.
In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score can be that the first and second features directly contact, or the first and second features are by intermediary mediate contact.And, fisrt feature second feature " on ", " top " and " above " but fisrt feature directly over second feature or oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " can be fisrt feature immediately below second feature or tiltedly below, or only represent that fisrt feature level height is less than second feature.
In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can combine in one or more embodiment in office or example in an appropriate manner.In addition, when not conflicting, the feature of the different embodiment described in this specification or example and different embodiment or example can carry out combining and combining by those skilled in the art.
Although illustrate and describe embodiments of the invention, those having ordinary skill in the art will appreciate that: can carry out multiple change, amendment, replacement and modification to these embodiments when not departing from principle of the present invention and aim, scope of the present invention is by claim and equivalents thereof.
Claims (17)
1. for a compressing mechanism for compressor, it is characterized in that, comprising: cylinder assembly and the bearing being located at the axial one end of described cylinder assembly, described cylinder assembly comprises cylinder, has compression chamber in described cylinder, and described bearing comprises:
Collar;
Flange part, described flange part is located between described collar and described cylinder assembly, and at described cylinder assembly axially, described flange part comprises the support axially relative with described cylinder assembly; And
Multiple first stiffening rib, each described first stiffening rib all extends along inward-outward direction and is located at the side away from described cylinder assembly of described support, the spaced apart distribution in the circumference of described support of described multiple first stiffening rib.
2. the compressing mechanism for compressor according to claim 1, it is characterized in that, described cylinder is formed with the vane slot extended along described cylinder radial direction, described first stiffening rib in described multiple first stiffening rib and described vane slot are oppositely arranged in the radial direction of described cylinder.
3. the compressing mechanism for compressor according to claim 2, it is characterized in that, the width of described first stiffening rib that the radial direction of described cylinder is oppositely arranged with described vane slot is greater than the width of all the other each described first stiffening ribs in described multiple first stiffening rib.
4. the compressing mechanism for compressor according to claim 2, it is characterized in that, cavity is limited, in the radial direction of described cylinder and the degree of depth of the described cavity of described first stiffening rib both sides that is oppositely arranged of the described vane slot degree of depth of described cavity that is less than in described multiple first stiffening rib to limit between the first stiffening rib described in all the other between two often adjacent the first stiffening ribs.
5. the compressing mechanism for compressor according to claim 1, it is characterized in that, described cylinder is formed with the suction port be communicated with described compression chamber, described at least one in described multiple first stiffening rib, the first stiffening rib is arranged the axially corresponding of described cylinder with described suction port.
6. the compressing mechanism for compressor according to claim 1, is characterized in that, described support has delivery valve seat, and the two ends on described delivery valve seat length direction are provided with described first stiffening rib.
7. the compressing mechanism for compressor according to any one of claim 1-6, is characterized in that, described bearing comprises further:
Second stiffening rib, described second stiffening rib is located at the side away from described cylinder assembly of described support and the circumference along described support extends.
8. the compressing mechanism for compressor according to claim 7, is characterized in that, described second stiffening rib comprises inner circumferential stiffening rib, and described inner circumferential stiffening rib is connected between described collar and described support.
9. the compressing mechanism for compressor according to claim 8, is characterized in that, along direction from inside to outside, the axial thickness of described inner circumferential stiffening rib reduces gradually.
10. the compressing mechanism for compressor according to claim 8, is characterized in that, described second stiffening rib comprises transition stiffening rib, and described transition stiffening rib is connected between the outer rim of described inner circumferential stiffening rib and the inner of described first stiffening rib.
11. compressing mechanisms for compressor according to claim 7, it is characterized in that, described second stiffening rib comprises periphery stiffening rib, described periphery stiffening rib is located between the outer rim of described support and the outer end of described first stiffening rib.
12. compressing mechanisms for compressor according to claim 11, is characterized in that, described periphery stiffening rib is formed with the mounting hole run through.
13. compressing mechanisms for compressor according to claim 12, is characterized in that, in the radial direction of described support, described mounting hole is corresponding with described first stiffening rib to be arranged.
14. compressing mechanisms for compressor according to claim 12, it is characterized in that, at described cylinder assembly axially, the side end face away from described cylinder assembly of described mounting hole is positioned at the side away from described cylinder assembly of described first stiffening rib.
15. compressing mechanisms for compressor according to claim 12, is characterized in that, described periphery stiffening rib is formed towards the installation base protruded away from described cylinder assembly direction, described mounting hole is formed on described installation base.
16. compressing mechanisms for compressor according to claim 12, is characterized in that, described periphery stiffening rib is formed with the installation deep gouge recessed towards described cylinder assembly direction, described mounting hole is formed on described installation deep gouge.
17. 1 kinds of compressors, is characterized in that, comprise the compressing mechanism for compressor according to any one of claim 1-16.
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| CN201510057915.0A CN104595190B (en) | 2015-02-04 | 2015-02-04 | Compressing mechanism for compressor and compressor with compressing mechanism |
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| CN201510057915.0A CN104595190B (en) | 2015-02-04 | 2015-02-04 | Compressing mechanism for compressor and compressor with compressing mechanism |
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| CN110439817A (en) * | 2019-09-12 | 2019-11-12 | 珠海凌达压缩机有限公司 | A kind of cylinder, pump assembly 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 |
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| CN104595190B (en) | 2017-02-22 |
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