CN105649984A - Compressing mechanism and low-backpressure rotary compressor - Google Patents
Compressing mechanism and low-backpressure rotary compressor Download PDFInfo
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- CN105649984A CN105649984A CN201610137502.8A CN201610137502A CN105649984A CN 105649984 A CN105649984 A CN 105649984A CN 201610137502 A CN201610137502 A CN 201610137502A CN 105649984 A CN105649984 A CN 105649984A
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- compression mechanism
- bearing assembly
- bent axle
- cylinder
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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
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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
- F04C29/02—Lubrication; Lubricant separation
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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 and a low-backpressure rotary compressor. The compressing mechanism comprises a bearing assembly, an air cylinder, a bent axle and a piston; the bearing assembly is provided with a center hole; the air cylinder is arranged on the bearing assembly and is provided with a compressing cavity and a sliding sheet groove communicating with the compressing cavity, and a groove is formed in the end face, opposite to the air cylinder, of the bearing assembly and communicates with the center hole; the bent axle penetrates through the center hole and the air cylinder and is provided with an eccentric part, and the eccentric part is located in the compressing cavity; the piston is arranged on the eccentric part in a sleeving mode and can roll along the inner wall of the compressing cavity. According to the compressing mechanism, the groove is formed in the end face, opposite to the air cylinder, of the bearing assembly and can store lubricating oil, the lubricating oil in the groove can flow into the part between the eccentric part and the bearing assembly when the compressing mechanism works, and therefore abrasion between the eccentric part and the bearing assembly can be effectively lowered, the friction noise can be lowered, and the service life of the compressing mechanism can be prolonged.
Description
Technical field
The present invention relates to technical field of refrigeration equipment, specifically, particularly relate to a kind of compression mechanism and low backpressure rotary compressor.
Background technology
Carbon-hydrogen refrigerant is as HCFC (HCFC class), such as R22, and HFC (hydrogen fluorohydrocarbon class), such as the alternative refrigerant of R410A or R407C, industry is paid close attention to the most. But, when carbon-hydrogen refrigerant is used for air-conditioner system, have a critically important problem, it is simply that it has high flammable, it is necessary to the cold-producing medium encapsulation amount of restriction hydrocarbon air conditioner device system.
Relative to the rotary compressor of high back pressure structure, there is the low back-pressure structure rotary compressor for connecting in low-pressure and housing in a kind of housing with pressure of inspiration(Pi). The content of the cold-producing medium in this low back pressure compressor can be greatly decreased, and makes the cold-producing medium encapsulation amount of refrigeration system to be greatly reduced.
But the existing complete relatively high back pressure compressor of low-pressure structure compressor performance is low, the reason affecting low back pressure compressor performance is piston end surface leakage, affects refrigerating capacity; The axle system operating relatively high back pressure compressor of oil viscosity is high, and friction loss strengthens and causes increasing into power. Affect performance factor based on two above, cause that low back pressure performance is difficult to promote.
Summary of the invention
It is contemplated that one of technical problem solved at least to a certain extent in correlation technique. For this, the present invention proposes a kind of compression mechanism, the advantage that described compression mechanism has high lubricating effect, serviceability is high.
The present invention also proposes a kind of low backpressure rotary compressor, and described low backpressure rotary compressor has above-mentioned compression mechanism.
Compression mechanism according to embodiments of the present invention, including: bearing assembly, described bearing assembly has centre bore; Cylinder, described cylinder is located on described bearing assembly, and described cylinder has compression chamber and the vane slot connected with described compression chamber, and end face relative with described cylinder on described bearing assembly is provided with groove, and described groove connects with described centre bore;Bent axle, described bent axle runs through described centre bore and described cylinder, and described bent axle has eccentric part, and described eccentric part is positioned at described compression chamber; And piston, described piston bush is located on described eccentric part and can roll along the inwall of described compression chamber.
Compression mechanism according to embodiments of the present invention, by the end face relative with cylinder at bearing assembly is provided with groove, lubricating oil can be stored in groove, when compressing mechanism when motion, lubricating oil in groove can be flowed between eccentric part and bearing assembly, thus can be effectively reduced the abrasion between eccentric part and bearing assembly, reduce friction noise, extend the service life of compression mechanism.
According to one embodiment of present invention, with the vertical median plane of described vane slot for datum level, around the central axis of described bent axle, according to counterclockwise described compression mechanism being divided into first quartile, the second quadrant, third quadrant and fourth quadrant, described groove minimum range respectively Lmin1, Lmin2, Lmin3 and Lmin4 in described first quartile to described fourth quadrant and between the periphery wall of described piston, and described Lmin1 >=2mm, described Lmin2 >=3mm, described Lmin3 >=4mm, described Lmin4 >=5mm.
According to one embodiment of present invention, the diameter of described centre bore is d, and the eccentric throw of described eccentric part is e, and the external diameter of described piston is D, and described Lmin1, described Lmin2, described Lmin3 and described Lmin4 meet following relation:
2mm��Lmin1��(D-d-e) mm;
3mm��Lmin2��(D-d-e) mm;
4mm��Lmin3��(D-d-e) mm;
5mm��Lmin4��(D-d-e)mm��
According to one embodiment of present invention, the end face of the close described cylinder of described centre bore has cannelure, described cannelure is d ' in the degree of depth in the radial direction of described centre bore, described cannelure connects with described groove, and described Lmin1, described Lmin2, described Lmin3 and described Lmin4 meet following relation:
2mm��Lmin1��(D-d-d '-e) mm;
3mm��Lmin2��(D-d-d '-e) mm;
4mm��Lmin3��(D-d-d '-e) mm;
5mm��Lmin4��(D-d-d��-e)mm��
According to one embodiment of present invention, described groove has the first end and the second end, described first end is in described first quartile, the line of the end points of described first end and the central axis of described bent axle is t, in the counterclockwise direction, it is �� that described first end is positioned at the upstream of described second end and described datum level to the angle of described straight line t, and described �� meets: 10 ��ܦ���90 ��.
According to one embodiment of present invention, the described groove degree of depth on the axis direction of described centre bore is h, and described h meets: 0.1mm��h��1mm.
According to one embodiment of present invention, described groove is become by camber line or linear structure at the outer contour of described cylinder end face upslide shadow.
According to one embodiment of present invention, being provided with a plurality of rib in described groove, a plurality of described rib is spaced apart along the length direction of described groove.
According to one embodiment of present invention, described bearing assembly includes: upper bearing (metal) and lower bearing, and described cylinder is folded between described upper bearing (metal) and described lower bearing, and described groove is located on the upper surface of described lower bearing and/or on the lower surface of described upper bearing (metal).
Low backpressure rotary compressor according to embodiments of the present invention, including: housing; And the compression mechanism described in upper, described compression mechanism is located in described housing.
Low backpressure rotary compressor according to embodiments of the present invention, by the end face relative with cylinder at bearing assembly is provided with groove, lubricating oil can be stored in groove, when compressing mechanism when motion, lubricating oil in groove can be flowed between eccentric part and bearing assembly, thus can be effectively reduced the abrasion between eccentric part and bearing assembly, reduce friction noise, extend the service life of compression mechanism.
Accompanying drawing explanation
Fig. 1 is low backpressure rotary compressor partial structurtes schematic diagram according to embodiments of the present invention;
Fig. 2 is the upward view of the upper bearing (metal) of compression mechanism according to embodiments of the present invention;
Fig. 3 is the close-up schematic view at A place in Fig. 2;
Fig. 4 is the cross-sectional schematic in Fig. 2 along B-B direction;
Fig. 5 is the upward view of the upper bearing (metal) of compression mechanism according to embodiments of the present invention;
Fig. 6 is the upward view of the upper bearing (metal) of compression mechanism according to embodiments of the present invention;
Fig. 7 is the close-up schematic view at C place in Fig. 6;
Fig. 8 is the upward view of the upper bearing (metal) of compression mechanism according to embodiments of the present invention;
Fig. 9 is the upward view of the upper bearing (metal) of compression mechanism according to embodiments of the present invention;
Figure 10 is the top view of the lower bearing of compression mechanism according to embodiments of the present invention;
Figure 11 is the top view of the lower bearing of compression mechanism according to embodiments of the present invention.
Accompanying drawing labelling:
Low backpressure rotary compressor 100,
Centre bore 111, groove 112, rib 113, cannelure 114, upper bearing (metal) 115, suction hole 123, lower bearing 116,
Cylinder 120, compression chamber 121, vane slot 122, slide plate 124, elastic component 125,
Bent axle 130, eccentric part 131, upper oil hole 132,
Piston 140,
Housing 150, oil sump 151, electric machine assembly 160,
Datum level m, the diameter of centre bore is d, and the eccentric throw of eccentric part is e, and the external diameter of piston is D, straight line t,
Cannelure is d ' in the degree of depth in the radial direction of centre bore, and the groove degree of depth on the axis direction of centre bore is h,
First quartile I, the second quadrant II, third quadrant III, fourth quadrant IV.
Detailed description of the invention
Being described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings. The embodiment described below with reference to accompanying drawing is illustrative of, it is intended to is used for explaining the present invention, and is not considered as limiting the invention.
Compression mechanism according to embodiments of the present invention is described in detail referring to Fig. 1-Figure 11.
As Figure 1-Figure 11, compression mechanism according to embodiments of the present invention, including: bearing assembly, cylinder 120, bent axle 130 and piston 140.
Specifically, bearing assembly has centre bore 111. Cylinder 120 is located on bearing assembly, and cylinder 120 has compression chamber 121 and the vane slot 122 connected with compression chamber 121. The end face relative with cylinder 120 of bearing assembly is provided with groove 112, is used for storing lubricating oil. Groove 112 connects with centre bore 111, and bearing assembly is provided with the suction hole 123 connected with compression chamber 121. Bent axle 130 runs through centre bore 111 and cylinder 120, and bent axle 130 has eccentric part 131, and eccentric part 131 is positioned at compression chamber 121, and piston 140 is set on eccentric part 131 and can roll along the inwall of compression chamber 121. Being provided with slide plate 124 in vane slot 122, in vane slot 122 slidably, the periphery wall of the head of slide plate 124 and piston 140 only supports slide plate 124, and the afterbody of slide plate 124 is offseted by elastic component 125 and cylinder 120.
Rotating to drive piston 140 to roll along the inwall of compression chamber 121 by bent axle 130, thus being compressed the coolant entered in compression chamber 121. The head (one end of the close bent axle 130 of slide plate 124) of slide plate 124 only supports with the periphery wall of piston 140, the afterbody (one end away from bent axle 130 of slide plate 124) of slide plate 124 can be connected with spring, thus, when piston 140 moves back and forth in compression chamber 121, slide plate 124 is mobile in vane slot 122 therewith, thus realizing the compression of coolant in compression chamber 121.
In the process of compression mechanism kinematic, in order to reduce the abrasion between two parts of relative motion, it is necessary to oil addition in compression mechanism. Such as, bent axle 130 is in the process rotated, and eccentric part 131 rotates relative to bearing assembly, in order to reduce the abrasion between eccentric part 131 and bearing assembly, it is necessary to oil addition between.By being provided with groove 112 on the end face relative with cylinder 120 of bearing assembly, lubricating oil can be stored in groove 112, and compression mechanism is in motor process, it is possible in time to oil addition between eccentric part 131 and bearing assembly.
Compression mechanism according to embodiments of the present invention, by being provided with groove 112 on the end face relative with cylinder 120 of bearing assembly, lubricating oil can be stored in groove 112, when compressing mechanism when motion, lubricating oil in groove 112 can be flowed between eccentric part 131 and bearing assembly, thus can be effectively reduced the abrasion between eccentric part 131 and bearing assembly, reduce friction noise, extend the service life of compression mechanism.
As shown in Fig. 2-Figure 11, according to one embodiment of present invention, with the vertical median plane of vane slot 122 for datum level m, around the central axis of bent axle 130, according to counterclockwise compression mechanism being divided into first quartile the I, second quadrant II, third quadrant III and fourth quadrant IV. Datum level m is all vertical with the upper and lower end face of cylinder 120 and datum level m divides equally vane slot 122 in the circumferential direction of bent axle 130. Suction hole 123 is positioned at first quartile, groove 112 minimum range in first quartile I to fourth quadrant IV and between the periphery wall of piston 140 respectively Lmin1, Lmin2, Lmin3 and Lmin4, and described Lmin1 >=2mm, described Lmin2 >=3mm, described Lmin3 >=4mm, described Lmin4 >=5mm. Thus, by making Lmin1 >=2mm, Lmin2 >=3mm, Lmin3 >=4mm, Lmin4 >=5mm can be effectively reduced the friction loss of compression mechanism, the serviceability of compression mechanism is promoted.
It should be noted that for convenience of describing, " counterclockwise " in the present invention each means: line centered by the central axis of bent axle 130, and (above-below direction as shown in Figure 1) is seen from the top down, around the direction that this centrage rotates counterclockwise. Such as, in Figure 10-Figure 11, shown in Figure 10-Figure 11 is the top view (schematic diagram seen when namely observing the end face coordinated with cylinder 120 of bearing assembly from the top down) of the end face coordinated with cylinder 120 of bearing assembly, and wherein arrow �� is oriented to the counter clockwise direction in the present invention; For another example, in Fig. 2-Fig. 3, Fig. 5-Fig. 9, what it was shown is the upward view (schematic diagram seen when namely observing the end face coordinated with cylinder 120 of bearing assembly from bottom to top) of the end face coordinated with cylinder 120 of bearing assembly, and wherein arrow �� ' is oriented to the counter clockwise direction in the present invention.
In example as shown in Figure 5, with the vertical center of the vane slot 122 at datum level m place for initial position p0, around the central axis of bent axle 130 along the direction shown in arrow �� ' by datum level m half-twist to primary importance p1 place, the region that datum level m turns over is first quartile I; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� ' from primary importance p1 half-twist to second position p2, and the region that datum level m turns over is the second quadrant II; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� ' from second position p2 half-twist to the 3rd position p3, and the region that datum level m turns over is third quadrant III; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� ' from the 3rd position p3 half-twist, and datum level m returns to initial position p0, and the region that datum level m turns over is fourth quadrant IV.
In example as shown in Figure 10, with the vertical center of the vane slot 122 at datum level m place for initial position q0, around the central axis of bent axle 130 along the direction shown in arrow �� by datum level m half-twist to primary importance q1 place, the region that datum level m turns over is first quartile I; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� from primary importance q1 half-twist to second position q2, and the region that datum level m turns over is the second quadrant II; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� from second position q2 half-twist to the 3rd position q3, and the region that datum level m turns over is third quadrant III; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� from the 3rd position q3 half-twist, and datum level m returns to initial position q0, and the region that datum level m turns over is fourth quadrant IV.
In first quartile I, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin1, described Lmin1 >=2mm; In the second quadrant II, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin2, described Lmin2 >=3mm; In third quadrant III, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin3, described Lmin3 >=4mm; In fourth quadrant IV, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin4, described Lmin4 >=5mm.
Further, the diameter of the centre bore 111 of bearing assembly is d, the eccentric throw of eccentric part 131 is e, and the external diameter of piston 140 is D, and described Lmin1, described Lmin2, described Lmin3 and described Lmin4 meet following relation: 2mm��Lmin1��(D-d-e) mm; 3mm��Lmin2��(D-d-e) mm; 4mm��Lmin3��(D-d-e) mm; 5mm��Lmin4��(D-d-e) mm. Thus can reduce the friction loss of compression mechanism further, promote the serviceability of compression mechanism.
In order to further reduce the friction loss of compression mechanism, in one embodiment of the invention, it is possible to offer cannelure 114 on the end face of the close cylinder 120 of centre bore 111. Thus, it is possible to the contact area efficiently reduced between bearing assembly and cylinder 120, reduce the friction loss of compression mechanism. Cannelure 114 is d ' in the degree of depth in the radial direction of centre bore 111, cannelure 114 connects with groove 112, and described Lmin1, described Lmin2, described Lmin3 and described Lmin4 meet following relation: 2mm��Lmin1��(D-d-d '-e) mm; 3mm��Lmin2��(D-d-d '-e) mm; 4mm��Lmin3��(D-d-d '-e) mm; 5mm��Lmin4��(D-d-d '-e) mm.
According to one embodiment of present invention, groove 112 has the first end and the second end, and the first end is in first quartile I, and the line of the central axis of the end points of the first end and bent axle 130 is t, in the counterclockwise direction, the first end is positioned at the upstream of the second end and the angle of datum level m to straight line t is ��. Here, the upstream of the second end " first end be positioned at " can refer in the counterclockwise direction rotation reference face m time, datum level m first passes through second end then through groove 112 of the first end on groove 112, such as, as shown in Figure 3, during along rotation reference face, direction m shown in arrow �� ', datum level m first passes through second end then through groove 112 of the first end on groove 112. Due at first quartile I in suction side, easily connecting with on high-tension side position near slide plate 124 side, for preventing high and low pressure side from leak, described �� is satisfied: 10 ��ܦ���90 ��.Such as, as shown in Fig. 2-Fig. 3, the end points of the first end of groove 112 is M, the end points of the second end of groove 112 is N, and groove 112 is distributed in first quartile the I, second quadrant II and third quadrant III, and end points M is in first quartile I, end points N is in third quadrant III, end points M is t to the straight line of bent axle 130 central axis, and the angle of datum level m to straight line t is �� in the counterclockwise direction, and described �� meets: 10 ��ܦ���90 ��.
As shown in Figure 4, in order to improve the oil storage capacity of groove 112, in one embodiment of the invention, the groove 112 degree of depth on the axis direction of centre bore 111 is h, and described h meets: 0.1mm��h��1mm. According to one embodiment of present invention, the outer contour that groove 112 projects on cylinder 120 end face is become by camber line or linear structure. It is to say, the side wall surface of groove 112 is arc-shaped curved surface or plane.
According to some embodiments of the present invention, being provided with a plurality of rib 113 in groove 112, a plurality of rib 113 is spaced apart along the length direction of groove 112. As it is shown in figure 9, be provided with two ribs 113 in groove 112, wherein a part for a rib 113 is positioned at first quartile I, and another part is positioned at the second quadrant II; A part for an other rib 113 is positioned at the second quadrant II, and another part is positioned at third quadrant III. Thus, the oil storage capacity of compression mechanism can not only be improved, it is also possible to strengthen the structural strength of bearing assembly.
As shown in Figure 1, according to some embodiments of the present invention, bearing assembly includes: upper bearing (metal) 115 and lower bearing 116, and cylinder 120 is folded between upper bearing (metal) 115 and lower bearing 116, and groove 112 is located on the upper surface of lower bearing 116 and/or on the lower surface of upper bearing (metal) 115. It is to say, bearing assembly can have a groove 112, this groove 112 can be located on the lower surface of upper bearing (metal) 115, it is also possible to is located on the upper surface of lower bearing 116; Bearing assembly can have two grooves 112, and one of them groove 112 can be located on the lower surface of upper bearing (metal) 115, and another groove 112 can be located on the upper surface of lower bearing 116.
Low backpressure rotary compressor 100 according to embodiments of the present invention as Figure 1-Figure 11, including: housing 150 with compress mechanism as above.
Specifically, the bottom of housing 150 is provided with oil sump 151, and compression mechanism is located in housing 150, and the bent axle 130 of compression mechanism has along the through upper oil hole 132 of its axis direction, and the lower end of bent axle 130 stretches in oil sump 151 after bearing assembly, cylinder 120.
Low backpressure rotary compressor 100 according to embodiments of the present invention, by being provided with groove 112 on the end face relative with cylinder 120 of bearing assembly, lubricating oil can be stored in groove 112, when compressing mechanism when motion, lubricating oil in groove 112 can be flowed between eccentric part 131 and bearing assembly, thus can be effectively reduced the abrasion between eccentric part 131 and bearing assembly, reduce friction noise, extend the service life of compression mechanism.
Low backpressure rotary compressor 100 according to embodiments of the present invention is described in detail with reference to the accompanying drawings with multiple specific embodiments. It is worth being understood by, described below is merely illustrative, rather than the concrete restriction to the present invention.
Embodiment 1
As Figure 1-Figure 5, in this embodiment, low backpressure rotary compressor 100 includes housing 150, electric machine assembly 160 and compression mechanism.
Specifically, the bottom of housing 150 is provided with oil sump 151, and compression mechanism and electric machine assembly 160 are each provided in housing 150, and electric machine assembly 160 is positioned at the top of housing 150 assembly.
Compression mechanism includes: bearing assembly, cylinder 120, bent axle 130, slide plate 124 and piston 140. Wherein, bearing assembly includes upper bearing (metal) 115 and lower bearing 116. Cylinder 120 has compression chamber 121 and the vane slot 122 connected with compression chamber 121. Cylinder 120 is folded between upper bearing (metal) 115 and lower bearing 116, and namely the lower surface of upper bearing (metal) 115 offsets with the upper surface of cylinder 120, and the lower surface of the upper surface of lower bearing 116 and cylinder 120 offsets. Upper bearing (metal) 115 and lower bearing 116 are respectively provided with centre bore 111. Upper bearing (metal) 115 is provided with suction hole 123, and suction hole 123 connects with compression chamber 121. Bent axle 130 has along the through upper oil hole 132 of its axis direction, and the lower end of bent axle 130 stretches to the bottom of housing 150 and is provided with in oil sump 151 after sequentially passing through the centre bore 111 of the centre bore 111 of upper bearing (metal) 115, cylinder 120 and lower bearing 116 from top to bottom.
The rotor of electric machine assembly 160 is connected with the upper end of bent axle 130, to drive bent axle 130 to rotate. Bent axle 130 has eccentric part 131, and eccentric part 131 is positioned at compression chamber 121, and piston 140 is set on eccentric part 131 and can roll along the inwall of compression chamber 121. Slide plate 124 is located in vane slot 122, and in vane slot 122 slidably, the periphery wall of the head of slide plate 124 and piston 140 only supports slide plate 124, and the afterbody of slide plate 124 is offseted by elastic component 125 (such as spring) and cylinder 120.
Piston 140 can be driven to roll along the inwall of compression chamber 121 by the rotation of bent axle 130, thus the coolant entered in compression chamber 121 is compressed. The head (one end of the close bent axle 130 of slide plate 124) of slide plate 124 only supports with the periphery wall of piston 140, the afterbody (one end away from bent axle 130 of slide plate 124) of slide plate 124 can be connected with spring, thus, when piston 140 moves back and forth in compression chamber 121, slide plate 124 is mobile in vane slot 122 therewith, thus realizing the compression of coolant in compression chamber 121.
The lower surface of upper bearing (metal) 115 is provided with the groove 112 for storing lubricating oil, and groove 112 connects with centre bore 111. As in figure 2 it is shown, the projection that groove 112 is on the upper surface of cylinder 120 is formed as crescent. In the process of compression mechanism kinematic, in order to reduce the abrasion between two parts that relative motion occurs, it is necessary to oil addition in compression mechanism. Such as, bent axle 130 is in the process rotated, and eccentric part 131 rotates relative to upper bearing (metal) 115, in order to reduce the abrasion between eccentric part 131 and upper bearing (metal) 115, it is necessary to oil addition between. By arranging groove 112 on the lower surface of upper bearing (metal) 115, lubricating oil can be stored in groove 112, and thus compression mechanism is in motor process, it is possible in time to oil addition between eccentric part 131 and upper bearing (metal) 115.
With the vertical median plane of vane slot 122 for datum level m, around the central axis of bent axle 130, according to counterclockwise compression mechanism being divided into first quartile I, the second quadrant II, third quadrant III and fourth quadrant IV. Datum level m is all vertical with the upper and lower end face of cylinder 120 and datum level m divides equally vane slot 122 in the circumferential direction of bent axle 130. Suction hole 123 is positioned at first quartile I, groove 112 minimum range in first quartile I to fourth quadrant IV and between the periphery wall of piston 140 respectively Lmin1, Lmin2, Lmin3 and Lmin4.
In first quartile I, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin1, described Lmin1 >=2mm; In the second quadrant II, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin2, described Lmin2 >=3mm; In third quadrant III, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin3, described Lmin3 >=4mm; In fourth quadrant IV, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin4, described Lmin4 >=5mm.
" counterclockwise " in this embodiment each means: (above-below direction as shown in Figure 1) is seen from the top down, line centered by the central axis of bent axle 130, around the direction that this centrage rotates counterclockwise. Such as, in Fig. 2-Fig. 3 and Fig. 5, what it was shown is the upward view (diagram seen when namely observing upper bearing (metal) 115 from bottom to top) of upper bearing (metal) 115, and wherein arrow �� ' is oriented to the counter clockwise direction in the present embodiment.
As shown in Figure 5, with the vertical center of the vane slot 122 at datum level m place for initial position p0, around the central axis of bent axle 130 along the direction shown in arrow �� ' by datum level m half-twist to primary importance p1 place, the region that datum level m turns over is first quartile I; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� ' from primary importance p1 half-twist to second position p2, and the region that datum level m turns over is the second quadrant II; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� ' from second position p2 half-twist to the 3rd position p3, and the region that datum level m turns over is third quadrant III; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� ' from the 3rd position p3 half-twist, and datum level m returns to initial position p0, and the region that datum level m turns over is fourth quadrant IV.
Further, the diameter of the centre bore 111 of upper bearing (metal) 115 is d, the eccentric throw of eccentric part 131 is e, and the external diameter of piston 140 is D, and described Lmin1, described Lmin2, described Lmin3 and described Lmin4 meet following relation: 2mm��Lmin1��(D-d-e) mm; 3mm��Lmin2��(D-d-e) mm; 4mm��Lmin3��(D-d-e) mm; 5mm��Lmin4��(D-d-e) mm. Thus can reduce the friction loss of compression mechanism further, promote the serviceability of compression mechanism.
Groove 112 has the first end and the second end, and the first end is in first quartile I, and the line of the central axis of the end points of the first end and bent axle 130 is t, and in the counterclockwise direction, the first end is positioned at the upstream of the second end and the angle of datum level m to straight line t is ��. here, the upstream of the second end " first end be positioned at " can refer in the counterclockwise direction rotation reference face m time, datum level m first passes through second end then through groove 112 of the first end on groove 112. as it is shown on figure 3, during along rotation reference face, direction m shown in arrow �� ', datum level m first passes through second end then through groove 112 of the first end on groove 112. due at first quartile I in suction side, easily connecting with on high-tension side position near slide plate 124 side, for preventing high and low pressure side from leaking, as shown in Fig. 2-Fig. 3, the end points of the first end of groove 112 is M, the end points of the second end of groove 112 is N, groove 112 is distributed in first quartile I, in second quadrant II and third quadrant III, end points M is in first quartile I, end points N is in third quadrant III, end points M is t to the straight line of bent axle 130 central axis, the angle of datum level m to straight line t is �� in the counterclockwise direction, and described �� meets: 10 ��ܦ���90 ��.
In order to improve the oil storage capacity of groove 112, the groove 112 degree of depth on the axis direction of centre bore 111 is h, and described h meets: 0.1mm��h��1mm.
Thus, by being provided with groove 112 on the lower surface of upper bearing (metal) 115, lubricating oil can be stored in groove 112, when compressing mechanism when motion, lubricating oil in groove 112 can be flowed between eccentric part 131 and bearing assembly, thus can be effectively reduced the abrasion between eccentric part 131 and bearing assembly, reduce friction noise, extend the service life of compression mechanism.
Embodiment 2
As Figure 6-Figure 8, as different from Example 1, in this embodiment, it is provided with cannelure 114 in the lower end of the centre bore 111 of upper bearing (metal) 115, cannelure 114 is d ' in the degree of depth in the radial direction of centre bore 111, cannelure 114 connects with groove 112, and described Lmin1, described Lmin2, described Lmin3 and described Lmin4 meet following relation: 2mm��Lmin1��(D-d-d '-e) mm; 3mm��Lmin2��(D-d-d '-e) mm; 4mm��Lmin3��(D-d-d '-e) mm; 5mm��Lmin4��(D-d-d '-e) mm. Thus, it is possible to the contact area efficiently reduced between upper bearing (metal) 115 and cylinder 120, thus reduce the friction loss of compression mechanism.
Embodiment 3
As it is shown in figure 9, as different from Example 1, in this embodiment, being provided with two ribs 113 in groove 112, wherein a part for a rib 113 is positioned at first quartile I, and another part is positioned at the second quadrant II; A part for an other rib 113 is positioned at the second quadrant II, and another part is positioned at third quadrant III. Thus, the oil storage capacity of compression mechanism can not only be improved, it is also possible to strengthen the structural strength of bearing assembly.
Embodiment 4
As shown in Figure 10, as different from Example 1, in this embodiment, groove 112 is formed on lower bearing 116, is namely formed with groove 112 on the upper surface of lower bearing 116.
As shown in Figure 10, with the vertical center of the vane slot 122 at datum level m place for initial position q0, around the central axis of bent axle 130 along the direction shown in arrow �� by datum level m half-twist to primary importance q1 place, the region that datum level m turns over is first quartile I; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� from primary importance q1 half-twist to second position q2, and the region that datum level m turns over is the second quadrant II; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� from second position q2 half-twist to the 3rd position q3, and the region that datum level m turns over is third quadrant III; Central axis around bent axle 130 makes datum level m along the direction shown in arrow �� from the 3rd position q3 half-twist, and datum level m returns to initial position q0, and the region that datum level m turns over is fourth quadrant IV.
In first quartile I, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin1, described Lmin1 >=2mm; In the second quadrant II, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin2, described Lmin2 >=3mm; In third quadrant III, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin3, described Lmin3 >=4mm; In fourth quadrant IV, the minimum range between the periphery wall of groove 112 and piston 140 is Lmin4, described Lmin4 >=5mm.
Further, the diameter of the centre bore 111 of lower bearing 116 is d, the eccentric throw of eccentric part 131 is e, and the external diameter of piston 140 is D, and described Lmin1, described Lmin2, described Lmin3 and described Lmin4 meet following relation: 2mm��Lmin1��(D-d-e) mm;3mm��Lmin2��(D-d-e) mm; 4mm��Lmin3��(D-d-e) mm; 5mm��Lmin4��(D-d-e) mm. Thus can reduce the friction loss of compression mechanism further, promote the serviceability of compression mechanism.
Embodiment 5
As shown in figure 11, as different from Example 4, in this embodiment, it is provided with cannelure 114 in the upper end of the centre bore 111 of lower bearing 116, cannelure 114 is d ' in the degree of depth in the radial direction of centre bore 111, cannelure 114 connects with groove 112, and described Lmin1, described Lmin2, described Lmin3 and described Lmin4 meet following relation: 2mm��Lmin1��(D-d-d '-e) mm; 3mm��Lmin2��(D-d-d '-e) mm; 4mm��Lmin3��(D-d-d '-e) mm; 5mm��Lmin4��(D-d-d '-e) mm. Thus, it is possible to the contact area efficiently reduced between lower bearing 116 and cylinder 120, thus reduce the friction loss of compression mechanism.
In describing the invention, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", " outward ", " clockwise ", " counterclockwise ", " axially ", " radially ", orientation or the position relationship of the instruction such as " circumference " are based on orientation shown in the drawings or position relationship, it is for only for ease of the description present invention and simplifies description, rather than the device of instruction or hint indication or element must have specific orientation, with specific azimuth configuration and operation, therefore it is not considered as limiting the invention.
Additionally, term " first ", " second " are only for descriptive purposes, and it is not intended that indicate or imply relative importance or the implicit quantity indicating indicated technical characteristic. Thus, define " first ", the feature of " second " can express or implicitly include at least one this feature. In describing the invention, " multiple " are meant that at least two, for instance two, three etc., 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, for instance, it is possible to it is fixing connection, it is also possible to be removably connect, or integral; Can be mechanically connected, it is also possible to be electrical connection or each other can communication; Can be joined directly together, it is also possible to be indirectly connected to by intermediary, it is possible to be connection or the interaction relationship of two elements of two element internals, unless otherwise clear and definite restriction. For the ordinary skill in the art, it is possible to understand above-mentioned term concrete meaning in the present invention 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 be merely representative of fisrt feature level height higher than second feature. Fisrt feature second feature " under ", " lower section " and " below " can be fisrt feature immediately below second feature or obliquely downward, or be merely representative of fisrt feature level height 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 in conjunction with this embodiment or example describe are contained at least one embodiment or the example of the present invention.In this manual, the schematic representation of above-mentioned term is necessarily directed to identical embodiment or example. And, the specific features of description, structure, material or feature can combine in one or more embodiments in office or example in an appropriate manner. Additionally, when not conflicting, the feature of the different embodiments described in this specification or example and different embodiment or example can be carried out combining and combining by those skilled in the art.
Although above it has been shown and described that embodiments of the invention, it is understandable that, above-described embodiment is illustrative of, it is impossible to be interpreted as limitation of the present invention, and above-described embodiment can be changed, revises, replace and modification by those of ordinary skill in the art within the scope of the invention.
Claims (10)
1. a compression mechanism, it is characterised in that including:
Bearing assembly, described bearing assembly has centre bore;
Cylinder, described cylinder is located on described bearing assembly, and described cylinder has compression chamber and the vane slot connected with described compression chamber, and end face relative with described cylinder on described bearing assembly is provided with groove, and described groove connects with described centre bore;
Bent axle, described bent axle runs through described centre bore and described cylinder, and described bent axle has eccentric part, and described eccentric part is positioned at described compression chamber; And
Piston, described piston bush is located on described eccentric part and can roll along the inwall of described compression chamber.
2. compression mechanism according to claim 1, it is characterized in that, with the vertical median plane of described vane slot for datum level, around the central axis of described bent axle, according to counterclockwise described compression mechanism being divided into first quartile, the second quadrant, third quadrant and fourth quadrant, described groove minimum range respectively Lmin1, Lmin2, Lmin3 and Lmin4 in described first quartile to described fourth quadrant and between the periphery wall of described piston, and described Lmin1 >=2mm, described Lmin2 >=3mm, described Lmin3 >=4mm, described Lmin4 >=5mm.
3. compression mechanism according to claim 2, it is characterised in that the diameter of described centre bore is d, and the eccentric throw of described eccentric part is e, and the external diameter of described piston is D, and described Lmin1, described Lmin2, described Lmin3 and described Lmin4 meet following relation:
2mm��Lmin1��(D-d-e) mm;
3mm��Lmin2��(D-d-e) mm;
4mm��Lmin3��(D-d-e) mm;
5mm��Lmin4��(D-d-e)mm��
4. compression mechanism according to claim 3, it is characterized in that, the end face of the close described cylinder of described centre bore has cannelure, described cannelure is d ' in the degree of depth in the radial direction of described centre bore, described cannelure connects with described groove, and described Lmin1, described Lmin2, described Lmin3 and described Lmin4 meet following relation:
2mm��Lmin1��(D-d-d '-e) mm;
3mm��Lmin2��(D-d-d '-e) mm;
4mm��Lmin3��(D-d-d '-e) mm;
5mm��Lmin4��(D-d-d��-e)mm��
5. compression mechanism according to claim 2, it is characterized in that, described groove has the first end and the second end, described first end is in described first quartile, the line of the end points of described first end and the central axis of described bent axle is t, in the counterclockwise direction, it is �� that described first end is positioned at the upstream of described second end and described datum level to the angle of described straight line t, and described �� meets: 10 ��ܦ���90 ��.
6. compression mechanism according to claim 1, it is characterised in that the described groove degree of depth on the axis direction of described centre bore is h, and described h meets: 0.1mm��h��1mm.
7. compression mechanism according to claim 1, it is characterised in that described groove is become by camber line or linear structure at the outer contour of described cylinder end face upslide shadow.
8. compression mechanism according to claim 1, it is characterised in that being provided with a plurality of rib in described groove, a plurality of described rib is spaced apart along the length direction of described groove.
9. the compression mechanism according to any one of claim 1-8, it is characterized in that, described bearing assembly includes: upper bearing (metal) and lower bearing, described cylinder is folded between described upper bearing (metal) and described lower bearing, and described groove is located on the upper surface of described lower bearing and/or on the lower surface of described upper bearing (metal).
10. a low backpressure rotary compressor, it is characterised in that including:
Housing; And
Compression mechanism according to any one of claim 1-9, described compression mechanism is located in described housing.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110985393A (en) * | 2019-10-28 | 2020-04-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Low-backpressure rotary compressor, corresponding oil return pressure drop control method and air conditioner |
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| JP2000179472A (en) * | 1998-12-16 | 2000-06-27 | Mitsubishi Electric Corp | Rotary compressor |
| CN105201830A (en) * | 2015-09-11 | 2015-12-30 | 广东美芝制冷设备有限公司 | Rotary compressor and compression mechanism thereof |
| CN204941961U (en) * | 2015-08-21 | 2016-01-06 | 广东美芝制冷设备有限公司 | Rotary compressor and there is its freezing cycle device |
| CN205714765U (en) * | 2016-03-10 | 2016-11-23 | 广东美芝制冷设备有限公司 | Compression mechanism and low backpressure rotary compressor |
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2016
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2000179472A (en) * | 1998-12-16 | 2000-06-27 | Mitsubishi Electric Corp | Rotary compressor |
| CN204941961U (en) * | 2015-08-21 | 2016-01-06 | 广东美芝制冷设备有限公司 | Rotary compressor and there is its freezing cycle device |
| CN105201830A (en) * | 2015-09-11 | 2015-12-30 | 广东美芝制冷设备有限公司 | Rotary compressor and compression mechanism thereof |
| CN205714765U (en) * | 2016-03-10 | 2016-11-23 | 广东美芝制冷设备有限公司 | Compression mechanism and low backpressure rotary compressor |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110985393A (en) * | 2019-10-28 | 2020-04-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Low-backpressure rotary compressor, corresponding oil return pressure drop control method and air conditioner |
| CN110985393B (en) * | 2019-10-28 | 2021-11-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Low-backpressure rotary compressor, corresponding oil return pressure drop control method and air conditioner |
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