CN104100532A - Rotary compressor and refrigeration cycle device with same - Google Patents
Rotary compressor and refrigeration cycle device with same Download PDFInfo
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- CN104100532A CN104100532A CN201410317259.9A CN201410317259A CN104100532A CN 104100532 A CN104100532 A CN 104100532A CN 201410317259 A CN201410317259 A CN 201410317259A CN 104100532 A CN104100532 A CN 104100532A
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Abstract
The invention discloses a rotary compressor and a refrigeration cycle device provided with the rotary compressor. The rotary compressor comprises an air cylinder component, two bearings and an exhausting device. A valve chamber is arranged on at least one bearing. The exhausting device comprises an exhaust valve, a limiting plate and a spring; an exhaust passage is defined between the peripheral wall of part of the exhaust valve and the inner peripheral wall of the valve cavity; the limiting plate is arranged inside the valve cavity and positioned in one side, far away from an exhaust vent, of the exhaust valve; the acting end of a spring is propped against the exhaust valve and the connecting end of the spring is propped against the limiting plate; the maximum value of the external diameter of the acting end of the spring is Ds, the maximum value of the distance between two points on the peripheral wall of the exhaust valve is Dv, the minimum value of the inner diameter of the valve cavity is Dc, and the Ds, the Dv and the Dc satisfy the relation as follows: 70 percent of the Dv is smaller than the Ds and the Ds is smaller than the Dc. According to the embodiment of the rotary compressor provided by the invention, the problem of delayed closing of the exhaust vent is solved so that airtightness of the exhaust vent is improved, the refrigerating capacity is enhanced, and power consumption is reduced.
Description
Technical field
The present invention relates to refrigerating field, especially relate to a kind of rotary compressor and there is its refrigerating circulatory device.
Background technique
The system of carrying rotary compressor is universal in the whole world, in order to improve its efficiency, the most important thing is to improve compressor and improves reliability.But rotary compressor has in the past used tongue type outlet valve for a long time.
The area of the valve accommodating groove of tongue type outlet valve is in the past large, and its bottom surface is also thin, so have the shortcoming that bearing rigidity declines.As it, improve countermeasure, in correlation technique, disclosed by outlet valve change into can knee-action free valve.Outlet valve, without fixing part, is opened the dull and stereotyped outlet valve that can carry out knee-action by Exhaust Gas.But there are the following problems for the outlet valve in correlation technique: on the one hand, outlet valve can produce due to the angle of swing of piston or the change of air displacement, thereby can cause vent closure to postpone to cause refrigerating capacity to decline.On the other hand, if increased the pressing force of spring, although the knee-action of outlet valve is stable, can produce overcompression loss.
Summary of the invention
The present invention is intended to solve at least to a certain extent one of technical problem in correlation technique.
For this reason, one object of the present invention is to propose a kind of rotary compressor, can improve the problem of late release of exhaust port to improve the sealing of exhaust port.
Another object of the present invention is to propose a kind of refrigerating circulatory device with above-mentioned rotary compressor.
Rotary compressor according to the embodiment of the present invention, comprising: cylinder assembly, and described cylinder assembly comprises the cylinder with compression chamber, two bearings, described two bearings are located at respectively on the upper surface and lower surface of described cylinder assembly, described at least one, bearing is provided with the valve pocket being communicated with described compression chamber and run through described bearing on thickness direction, and one end towards described compression chamber of described valve pocket limits exhaust port, venting gas appliance, described venting gas appliance comprises outlet valve, limiting board and spring, described outlet valve is located in described valve pocket to open or close described exhaust port, between the part periphery wall of described outlet valve and the inner circle wall of described valve pocket, limit exhaust passage, described limiting board be located in described valve pocket and the side away from described exhaust port that is positioned at described outlet valve to limit the moving displacement of described outlet valve, the motion end of described spring is only against on described outlet valve, the connecting end of described spring is only against on described limiting board, the maximum value of the external diameter of the motion end of wherein said spring is Ds, the maximum value of the distance between 2 of the periphery wall of described outlet valve is Dv, the minimum value of the internal diameter of described valve pocket is Dc, described Ds, Dv, between Dc, meet following relation: 70%Dv < Ds < Dc.
According to the rotary compressor of the embodiment of the present invention, can improve the problem of late release of exhaust port to improve the sealing of exhaust port, improve refrigerating capacity, reduce power consumption.
In addition, rotary compressor according to the above embodiment of the present invention can also have following additional technical characteristics:
In some embodiments of the invention, the cross section of described valve pocket is circular, described outlet valve be configured to and the inner circle wall of described valve pocket between limit a plurality of exhaust passages spaced apart in circumferential direction.
Alternatively, described exhaust passage is 3～6.
Preferably, described a plurality of exhaust passage is evenly spaced apart.
In other embodiments of the present invention, the cross section of described valve pocket forms regular polygon, and described outlet valve forms circular plate.
Alternatively, described spring is line style spring or non-linear spring.
According to a particular embodiment of the invention, described outlet valve is a plurality of and superposes on above-below direction.
Particularly, described valve pocket is sintered alloy profiled member or forging method profiled member.
According to some embodiments of the present invention, described outlet valve is provided with a plurality of transom windows, and described in each, transom window runs through described outlet valve at the thickness direction of described outlet valve.
According to the refrigerating circulatory device of the embodiment of the present invention, comprise rotary compressor according to the above embodiment of the present invention.
Accompanying drawing explanation
Fig. 1 is relevant with embodiments of the invention 1, represents the longitudinal section of the inside of rotary compressor;
Fig. 2 is correlated with embodiment 1, the planimetric map of the valve pocket configuring on main bearing;
Fig. 3 is correlated with embodiment 1, forms the component diagram of venting gas appliance;
Fig. 4 is with embodiment 1 sectional view relevant, that represent venting gas appliance;
Fig. 5 is with embodiment 1 details drawing relevant, that represent venting gas appliance;
Fig. 6 is with embodiment 1 that be correlated with, outlet valve ability of posture control related description figure;
Fig. 7 is with embodiment 1 that be correlated with, outlet valve ability of posture control related description figure;
Fig. 8 is with relevant, relevant to the ability of posture control of the outlet valve cases of design in the past of embodiment 1;
Fig. 9 is with the embodiment of the present invention 2 component diagram relevant, non-linear spring;
Figure 10 is with embodiment 2 performance plot relevant, non-linear spring;
Figure 11 is with the embodiment of the present invention 3 design example relevant, regular polygon valve pocket;
Figure 12 is with embodiment 3 design example relevant, regular polygon valve pocket and outlet valve.
Embodiment
Describe embodiments of the invention below in detail, described embodiment's example is shown in the drawings, and wherein same or similar label represents same or similar element or has the element of identical or similar functions from start to finish.Below by the embodiment who is described with reference to the drawings, be exemplary, be intended to for explaining the present invention, and can not be interpreted as limitation of the present invention.
In description of the invention, it will be appreciated that, term " " center ", " longitudinally ", " laterally ", " 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 indications such as " circumferentially " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, rather than device or the element of indication or hint indication must have specific orientation, with specific orientation structure and operation, therefore can not be interpreted as limitation of the present invention.
In addition, term " first ", " second " be only for describing object, and can not be interpreted as indication or hint relative importance or the implicit quantity that indicates indicated technical characteristics.Thus, one or more these features can be expressed or impliedly be comprised to the feature that is limited with " first ", " second ".In description of the invention, the implication of " a plurality of " is two or more, unless otherwise expressly limited specifically.
In the present invention, unless otherwise clearly defined and limited, the terms such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and for example, can be to be fixedly connected with, and can be also to removably connect, or be integral; Can be mechanical connection, can be to be also electrically connected to; Can be to be directly connected, also can indirectly 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, can understand as the case may be above-mentioned term concrete meaning in the present invention.
Below with reference to Fig. 1-Figure 12, describe in detail according to the rotary compressor of the embodiment of the present invention, wherein rotary compressor can be single cylinder rotary compressor or twin-tub rotation-type compressor, and rotary compressor can also vertical compressor, horizontal compressor, wave rotary compressor, housing low pressure formula rotary compressor or 2 stage compressors.Rotary compressor can be applied in the freezing cycle devices such as aircondition, refrigeration plant or water heater.
Rotary compressor according to the embodiment of the present invention, comprising: cylinder assembly, two bearings and venting gas appliance, wherein, cylinder assembly comprises the cylinder 40 with compression chamber 41.Two bearings are located at respectively on the upper surface and lower surface of cylinder assembly, and at least one bearing is provided with that be communicated with compression chamber 41 and on thickness direction, runs through the valve pocket 12 of bearing, and one end towards compression chamber 41 of valve pocket 12 limits exhaust port 13.In other words, two bearings are respectively main bearing 50 and supplementary bearing 55, and main bearing 50 is located at the upper surface of cylinder assembly, and supplementary bearing 55 is located at the lower surface of cylinder assembly, and main bearing 50 and/or supplementary bearing 55 are provided with valve pocket 12, and valve pocket 12 is communicated with compression chamber 41.
Venting gas appliance comprises outlet valve 20, limiting board 30 and spring 35, outlet valve 20 is located in valve pocket 12 to open or close exhaust port 13, between the part periphery wall of outlet valve 20 and the inner circle wall 12a of valve pocket 12, limit exhaust passage, limiting board 30 is located in valve pocket 12 and is positioned at the side away from exhaust port 13 of outlet valve 20 with the moving displacement of restriction outlet valve 20, the motion end of spring 35 is only against on outlet valve 20, the connecting end of spring 35 is only against on limiting board 30, the maximum value of the external diameter of the motion end of its medi-spring 35 is Ds, the maximum value of the distance between 2 of the periphery wall of outlet valve 20 is Dv, the minimum value of the internal diameter of valve pocket 12 is Dc, Ds, Dv, between Dc, meet following relation: 70%Dv < Ds < Dc.
Under the impulse force of the pressurized gas of compression chamber 41 interior compressions, outlet valve 20 is opened exhaust port 13, and the pressurized gas that are drained in exhaust port 13 are drained in valve pocket 12 from exhaust passage.
According to the rotary compressor of the embodiment of the present invention, can improve the problem of late release of exhaust port to improve the sealing of exhaust port, improve refrigerating capacity, reduce power consumption.
In some embodiments of the invention, as shown in Figures 2 and 3, the cross section of valve pocket 12 is circular, outlet valve 20 be configured to and the inner circle wall of valve pocket 12 between limit a plurality of exhaust passages spaced apart in circumferential direction.Alternatively, exhaust passage is 3～6.Preferably, a plurality of exhaust passages are evenly spaced apart.
In other embodiments of the present invention, the cross section of valve pocket 12 forms regular polygon, and outlet valve 20 forms circular plate.
In some embodiments of the invention, outlet valve 20 is a plurality of and superposes on above-below direction.
Particularly, valve pocket 12 is sintered alloy profiled member or forging method profiled member.Thereby be convenient to the machine shaping of valve pocket 12.
As shown in figure 12, in some embodiments of the invention, outlet valve 20 is provided with a plurality of transom window 20d, and each transom window 20d runs through outlet valve 20 at the thickness direction of outlet valve 20.Thereby can enlargement gas passage, there is the effect of improving exhaust resistance and noise.
According to the refrigerating circulatory device of the embodiment of the present invention, comprise rotary compressor according to the above embodiment of the present invention.
Below with reference to Fig. 1-Figure 12, describe the rotary compressor of several specific embodiments according to the present invention in detail.
Embodiment 1:
The form of the embodiment of the present invention 1 describes according to Fig. 1.
Rotary compressor 1 by be fixed on compression mechanical part 4 on the internal diameter of housing 2 with and the motor portion 3 of top configuration form.In the compression chamber 41 that compression mechanical part 4 possesses cylinder 40, form in this cylinder, carry out eccentric operating piston 45, with this piston carry out synchronous reciprocating motion slide plate (without diagram), make the eccentric shaft 60 of piston 45 eccentric drive, to this eccentric shaft slides main bearing 50 and the supplementary bearing 55 of support.
Main bearing 50 and supplementary bearing 55 by long bearing 50a and main bearing flange 50b, minor axis, hold 55a respectively and supplementary bearing flange 55b forms.Long bearing 50a and minor axis hold 55a and eccentric shaft 60 carries out sliding support.Main bearing flange 50b and supplementary bearing flange 55b are fixed in cylinder 40, form the compression chamber 41 of sealing together with cylinder 40.
Venting gas appliance 10 of the present invention can be configured in a side or the both sides of main bearing flange 50b or supplementary bearing flange 55b, in embodiment 1, has configured venting gas appliance 10, at an upper portion thereof exhaust silencer 51 has been installed in main bearing flange 50b.
The same with common rotary compressor, in compression chamber 41, the pressurized gas of compression are by being discharged to exhaust silencer 51 from valve pocket 12 exhaust port 13 of compression chamber 41 openings.From outlet pipe (without diagram) be out discharged to refrigeration plant thereafter.Therefore, the internal pressure of housing 2 is high pressure side.
Explanation venting gas appliance 10 before, first, the design structure of venting gas appliance 10 is described.
Fig. 2 is the planimetric map of valve pocket 12.Valve pocket 12 is round cylinder slots of processing on main bearing flange 50b, and its internal diameter is Dc.In the bottom centre of valve pocket 12, possess the circular exhaust port 13 of compression chamber 41 openings, its valve seat 14 of processing around.In addition, at interior all 12a of valve pocket 12, possesses circular restraining groove 15 (having diagram in Fig. 5).As a reference, the position of the internal diameter of compression chamber 41 and slide plate 46 dots.
The inside opening of about 80～100% pairs of compression chambers 41 in the general design of exhaust port 13, the remaining outside opening to compression chamber 41.In the design of Fig. 2, the inside opening of about 95% pair of compression chamber 41 of the opening area of exhaust port 13.In addition, as shown in Figure 1, exhaust port 13 is not standard-sized sheet conventionally, and owing to carrying out the passing through of upper-end surface of the piston 45 of eccentric operating in compression chamber 41, each opening area turning changes between 100～0%.
In Fig. 3, press order from the bottom up, represent outlet valve 20, coil spring 35, limiting board 30.Outlet valve 20 is by 4 jut 20a that are configured according to the angle of 90 degree respectively and curved part 20b forms, thickness of slab is the flat board of 0.2～0.3mm left and right.The tip of jut 20a is separately on the circle of diameter Dv.Therefore, between the internal diameter (Dc) of the tip of jut 20a and valve pocket 12, have little gap, such as the glade plane space of 20～100 about μ m.Therefore, outlet valve 20, due to the actuating range that 4 jut 20a have limited substantially horizontal, can move up and down in valve pocket 12.
The opening portion forming between interior all 12a of each curved part 20b and valve pocket is from exhaust port 13 exhaust passage out, so the area of the enlarged openings portion that will try one's best.In addition, the scope of 3～6 that the quantity of jut 20a preferably uniformly-spaced configures.
Columnar coil spring 35, its external diameter are that Ds, wire diameter are d.But, as described later, can use circular cone coil spring etc.Limiting board 30 is used the C type shelves ring that possesses opening portion 30a.But, also can use lining nut that CR shape shelves ring or hole use etc. to omit restraining groove 15 (Fig. 5).
In valve pocket 12 shown in Fig. 2, inserted that outlet valve 20 and coil spring 35, limiting board 30 are pressed into after restraining groove 15, the venting gas appliance 10 shown in Fig. 4 completes on main bearing flange 50b.Fig. 5 represents planimetric map and the sectional view of venting gas appliance 10.In addition, in the planimetric map of Fig. 5, the opening portion that expands limiting board 30 represents the position of coil spring 35.
In Fig. 5, coil spring 35 is between outlet valve 20 and limiting board 30, and outlet valve 20 is pressed on valve seat 14.Meanwhile, coil spring 35, by its telescopic action, when outlet valve 20 rises, prevents that outlet valve 20 from directly colliding on limiting board 30.That is, coil spring 35 not only determines the actuating range of outlet valve 20, by its buffer function, can prevent that the breakage of outlet valve 20 and noise from occurring.
The present invention is the spread loop springs 35 of trying one's best from the viewpoint feature of the ability of posture control of outlet valve 20.Such as, in the design of the domestic air conditioning of extensive use rotary compressor, the aperture of exhaust port 13 is approximately 7mm.Now, the internal diameter of valve pocket 12 (Dc) is 15mm, and the external diameter of coil spring 35 (Ds) is considered form error, and it is also passable that maximum is arranged on 14.8mm.At this moment, wire diameter (d) is so be that 0.2～0.3mm left and right is because the air resistance that wire diameter size produces is the scope that can not ignore.In addition, the limiting board 30 that the external diameter of large coil spring 35 and internal diameter are large makes gas channel maximum, has the effect of improving air resistance loss.
In Fig. 6, the angle of swing (θ) of piston 45 or eccentric shaft 60b in advance, represents the moment that gas exhaust starts while spending such as θ=150.At this moment, exhaust port 13 standard-sized sheets, exhaust is in the full field of exhaust port 13 average flow.Therefore, outlet valve 20 is on average shunted to 4 gas channel 20c with the parallel floating of valve seat 14, exhaust, from the internal diameter of coil spring 35, from the upper end of valve pocket 12, discharges.
In Fig. 7, the angle of swing of piston 45 in advance, discharge by the gas while spending such as expression θ=270.So the aperture of exhaust port 13 is approximately low to inclined to one side exhaust port 13 flows outside of approximately 50% exhaust.But, the parallelism of outlet valve 20 can keep substantially, exhaust is shunted coequally in 4 gas channel 20c.Its reason is that the periphery of coil spring 35 has been pushed down the maximum outside diameter part of outlet valve 20, just very large to the moment of outlet valve 20 effects like this.
The angle of rotation of piston 45 further shifts to an earlier date, such as the moment compression chamber of θ=360 or 0 degree 41 can be switched to low pressure.So this, compression chamber low voltage side outlet valve 20 that all switches to of 41 needed valve seat 14 contract fullys moment.The present invention, because the inclination that the knee-action of outlet valve 20 brings is less, so the speed of full cut-off.
On the other hand, in design as less in the external diameter of Fig. 8, coil spring 35, in the degree of θ=270, the moment that acts on outlet valve 20 diminishes, therefore, the inclination of outlet valve 20 can strengthen.Therefore, the moment of θ=360 or 0 degree, the delay of closing that can produce valve seat 14.
The full cut-off speed of valve seat 14 has a great impact the performance of compressor.The slow-footed words of full cut-off, owing to starting to cause refrigerating capacity to decline to the high pressure gas leakage of compression chamber 41 from valve pocket 12, and power consumption can increase.That is,, due to expanding again of pressurized gas, can produce gettering quantity and reduce (refrigerating capacity decline) and compression power increase (power consumption increase).Therefore, COP can decline.COP while particularly carrying the high speed operation of rotary compressor of variable-frequency motor declines significantly.
According to the experimental result of air-conditioning inverter controlled rotary compressor, the external diameter of coil spring 35 (Ds) compares during 10.0mm for (A) 14.8mm with (B), is 1.2%, when the 120rps of High Rotation Speed is 4.6%, COP separately declines when being 30rps with respect to (A) compressor rotary speed (B).That is, after high speed operation, the valve seat 14 bringing due to outlet valve 20 to close delay more remarkable.In addition, the words of the external diameter of outlet valve 20 (Dv)=15mm are, the Ds/Dv=0.67 of the Ds/Dv=0.98 of (A), (B).
But when using constant-seed motor (50 or 60rps), more above-mentioned (A) and (B), COP differs from 2%.Therefore, even Ds/Dv=0.67 is also operable in the time of can judging constant-seed motor.
From these data, even if design condition of the present invention if the words Ds/Dv=0.7COP of Ds/Dv≤0.7% declines is also in allowed band.Consider in the words of the just polygonal valve pocket that embodiment 3 discloses, above-mentioned design condition in addition,, " maximum outside diameter of the motion end of coil spring 35 is 70% larger than the Extreme breadth of outlet valve 20, less than the minimum width of valve pocket 12.", describe so properer.
In addition, the ratio of Ds/Dv is little resembling 0.7, uses circular cone coil spring (Fig. 9) can make path side use in limiting board 30 sides in outlet valve 20 sides, large footpath side.In above-mentioned design, so need exhaust to pass through internal side diameter coil spring intermediate demand gap from the outside diameter of circular cone coil spring.But, use lining nut for CR shape shelves ring or hole, also can use cylinder coil spring.
In addition, as the valve seat that improves outlet valve, close the method for delay, can increase the elastic force of coil spring 35, increase the moment of outlet valve 20.If but increased elastic force, power consumption could increase, so COP can decline.Therefore, resemble the present invention so as far as possible spread loop spring 35 external diameter (Ds), make the design of elastic force minimum best.
The external diameter of spread loop spring 35, coil spring 35 contacts with valve pocket 12 in interior week, may produce wearing and tearing.But as the feature of the principle aspect of rotary compressor, from compression chamber 41 exhaust out, comprised the oil of 3～5% left and right, so, to coil spring 35, outlet valve 20, can lubricate fully, also no problem to their abrasion aspect.
Embodiment 2:
Lift-launch can the comfortable rotary compressor that switches the variable-frequency motor of compressor rotary speed, and the rotating speed by 20～120Hz changes, and air displacement probably increases by 6 times of left and right.Therefore, the change of the path increment of outlet valve 20 (S, Fig. 6) also increases.On the other hand, path increment (S) increases, and the inclination of outlet valve can increase, so the full cut-off speed of valve seat can be slack-off, as mentioned above, produces the problem that COP declines.
As the solution of this problem, embodiment 2 has used non-linear spring, reduces the change of the path increment (S) of outlet valve.Fig. 9 is the cases of design of non-linearity coil spring.Figure A is cylinder type coil spring, towards the right side tooth pitch of figure, is reducing.Therefore, the load increase along with spring motion end, starts to compress from the little side of tooth pitch, so spring constant can increase.Figure B is cone type coil spring.Along with the load increase of coil-end, from coil footpath, a large side starts to compress, or is accommodated in the large internal diameter in coil footpath, so spring constant can increase.
Figure 10 conceptually represent line style coil spring 1. with the comparison 2. of non-linear line coil spring.S is that the stroke of outlet valve 20 is long, S1 and S2 are respectively that coil spring range 1. and is 2. long, F is that the spring force (loading), F1 and the F2 that act on outlet valve 20 is the stroke length of outlet valve 20 when being 0, acts on the initial stage load on coil spring separately.
2. non-linearity coil spring increases at the path increment of outlet valve 20, when coil spring starts to compress, together with the stroke of spring constant and outlet valve 20 is long, increases.That is, the size long to stroke is directly proportional, and spring constant can increase, so can increase the load of outlet valve 20.Therefore,, when control non-linearity coil spring stroke long (S) is 2. excessive, even in the situation that stroke is grown up width increase, also there is the effect of the posture of stable outlet valve 20.
Embodiment 3:
The cylinder that valve pocket 12 its cross sections of embodiment 1 are comprised of circle, even but the cross section of the such valve pocket 12 of Figure 11 is that square, outlet valve 21 are circular, can bring into play effect similarly to Example 1.In this design, possess 4 gas channel 20c.In addition, the cross section of valve pocket 12 is that equilateral triangle is also passable.
Outlet valve 20 of the present invention be shaped as circle, so can use by overlapping several pieces valve blocks.This design middle valve plate reduced thickness, also can improve the compression of valve seat 52, thus Leakage Gas minimizing, the effect that compressor efficiency is improved.The outlet valve reduced thickness that in addition, can make to drop on valve seat 14 further improves sealing.In addition, the shape of outlet valve 20 small-sized simple (circle) in the present invention, so do not worry that fatigue ruption causes that valve block is damaged completely.
And even the cross section regular hexagon of valve pocket 12 as shown in figure 12, the action of outlet valve 21 is also no problem, the quantity of polygonal gas channel 20c can increase, and the gross area can reduce.But as shown in figure 12, if append transom window 20d in outlet valve 22, can enlargement gas passage.Possessing the outlet valve 20 that the outlet valve 22 of transom window 20d can alternate embodiment 1 uses.And valve pocket 12 chamfering 25 is around the chamferings of appending in the upper, open end of valve pocket 12, has and improves the exhaust resistance of exhaust and the effect of noise.
The design condition aspect of embodiment 1 and 2 coil springs 35 that disclose, embodiment 3 also can use.In addition, from the present invention of embodiment's 1 to 3 announcement, can the multi-cylinder rotary compressors such as twin-tub, 2 pole compression rotary compressors, adopt.In addition, in embodiment 3, the valve pocket of the regular polygon of explanation is not cylinder type, so although there is shortcoming processability aspect, if bearing carries out moulding with sintered alloy or forging, just can solve the problem of manufacturing.
By embodiment 1 to 3, valve pocket 12 of the present invention is compared with tongue type valve exhaust device in the past, significantly realizes miniaturization, and processing and assembling are than being easier to.Therefore, the problem of bearing rigidity in the past still not, manufacturing and manufacture cost also can be improved.And, by outlet valve 20 and the design optimization of controlling the spring 35 of this action and posture, prove and can reach and the equal above efficiency of tongue type valve exhaust device and noise performance in the past.In addition, believe by the feature of outlet valve 20 light weights, the optimization of the employing of non-linear spring, detailing has the potentiality of further improving performance.
Adopt rotary compressor of the present invention in air conditioner, refrigeration plant, water heater etc., to use.In addition, the present invention also can apply in housing low pressure formula rotary compressor.In addition, venting gas appliance of the present invention is easily manufactured, so the value in industry is large.
In sum, according to the rotary compressor tool of the specific embodiment of the invention, have the following advantages:
(1) coil spring external diameter increases, and presses and presses outlet valve, so due to the improvement of exhaust port sealing, refrigerating capacity rises, power consumption also reduces.
(2) by adopting non-linear spring, little gas pressure outlet valve just can opening.In addition, can control excessive valve block stroke, so because the speed of outlet valve exhaust port sealing can be accelerated.Therefore, performance improvement effect can further significantly be improved.
(3) by the limiting board of the interior week configuration annulus at valve pocket, can improve assembling performance.In addition, exhaust resistance also can reduce.
(4) the present invention can be widely used in duplex-cylinder rotary compressor or 2 stage compressors.
In the present invention, unless otherwise clearly defined and limited, First Characteristic Second Characteristic " 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, First Characteristic Second Characteristic " on ", " top " and " above " but First Characteristic directly over Second Characteristic or oblique upper, or only represent that First Characteristic level height is higher than Second Characteristic.First Characteristic Second Characteristic " under ", " below " and " below " can be First Characteristic under Second Characteristic or tiltedly, or only represent that First Characteristic level height is less than Second Characteristic.
In the description of this specification, the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to be contained at least one embodiment of the present invention or example in conjunction with specific features, structure, material or the feature of this embodiment or example description.In this manual, to the schematic statement of above-mentioned term not must for be identical embodiment or example.And, the specific features of description, structure, material or feature can one or more embodiments in office or example in suitable mode combination.In addition,, not conflicting in the situation that, those skilled in the art can carry out combination and combination by the feature of the different embodiments that describe in this specification or example and different embodiment or example.
Although illustrated and described embodiments of the invention above, be understandable that, above-described embodiment is exemplary, can not be interpreted as limitation of the present invention, and those of ordinary skill in the art can change above-described embodiment within the scope of the invention, modification, replacement and modification.
Claims (10)
1. a rotary compressor, is characterized in that, comprising:
Cylinder assembly, described cylinder assembly comprises the cylinder with compression chamber;
Two bearings, described two bearings are located at respectively on the upper surface and lower surface of described cylinder assembly, described at least one, bearing is provided with the valve pocket being communicated with described compression chamber and run through described bearing on thickness direction, and one end towards described compression chamber of described valve pocket limits exhaust port;
Venting gas appliance, described venting gas appliance comprises outlet valve, limiting board and spring, described outlet valve is located in described valve pocket to open or close described exhaust port, between the part periphery wall of described outlet valve and the inner circle wall of described valve pocket, limit exhaust passage, described limiting board be located in described valve pocket and the side away from described exhaust port that is positioned at described outlet valve to limit the moving displacement of described outlet valve, the motion end of described spring is only against on described outlet valve, the connecting end of described spring is only against on described limiting board, the maximum value of the external diameter of the motion end of wherein said spring is Ds, the maximum value of the distance between 2 of the periphery wall of described outlet valve is Dv, the minimum value of the internal diameter of described valve pocket is Dc, described Ds, Dv, between Dc, meet following relation: 70%Dv < Ds < Dc.
2. rotary compressor according to claim 1, is characterized in that, the cross section of described valve pocket is circular, described outlet valve be configured to and the inner circle wall of described valve pocket between limit a plurality of exhaust passages spaced apart in circumferential direction.
3. rotary compressor according to claim 2, is characterized in that, described exhaust passage is 3～6.
4. rotary compressor according to claim 2, is characterized in that, described a plurality of exhaust passages are evenly spaced apart.
5. rotary compressor according to claim 1, is characterized in that, the cross section of described valve pocket forms regular polygon, and described outlet valve forms circular plate.
6. rotary compressor according to claim 1, is characterized in that, described spring is line style spring or non-linear spring.
7. rotary compressor according to claim 1, is characterized in that, described outlet valve is a plurality of and superposes on above-below direction.
8. rotary compressor according to claim 1, is characterized in that, described valve pocket is sintered alloy profiled member or forging method profiled member.
9. rotary compressor according to claim 1, is characterized in that, described outlet valve is provided with a plurality of transom windows, and described in each, transom window runs through described outlet valve at the thickness direction of described outlet valve.
10. a refrigerating circulatory device, is characterized in that, comprises according to the rotary compressor described in any one in claim 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201410317259.9A CN104100532B (en) | 2014-07-04 | 2014-07-04 | Rotary compressor and the refrigerating circulatory device with which |
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| CN201410317259.9A CN104100532B (en) | 2014-07-04 | 2014-07-04 | Rotary compressor and the refrigerating circulatory device with which |
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| CN104100532A true CN104100532A (en) | 2014-10-15 |
| CN104100532B CN104100532B (en) | 2017-03-29 |
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| CN201410317259.9A Active CN104100532B (en) | 2014-07-04 | 2014-07-04 | Rotary compressor and the refrigerating circulatory device with which |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114851322A (en) * | 2022-05-18 | 2022-08-05 | 西南林业大学 | Hot pressing method for continuous flat-pressing thick artificial board |
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| CN102235357A (en) * | 2010-05-07 | 2011-11-09 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN102748297A (en) * | 2011-04-21 | 2012-10-24 | 广东美芝制冷设备有限公司 | Compressor exhaust apparatus |
| CN102996457A (en) * | 2012-12-03 | 2013-03-27 | 珠海格力电器股份有限公司 | Rotary compressor and exhaust valve |
| CN204239263U (en) * | 2014-07-04 | 2015-04-01 | 广东美芝制冷设备有限公司 | Rotary compressor and there is its refrigerating circulatory device |
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| JP2001323881A (en) * | 2000-05-16 | 2001-11-22 | Hitachi Ltd | Compressor |
| JP2004360491A (en) * | 2003-06-02 | 2004-12-24 | Calsonic Compressor Seizo Kk | Relief valve and gas compressor |
| CN102235357A (en) * | 2010-05-07 | 2011-11-09 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN102748297A (en) * | 2011-04-21 | 2012-10-24 | 广东美芝制冷设备有限公司 | Compressor exhaust apparatus |
| CN102996457A (en) * | 2012-12-03 | 2013-03-27 | 珠海格力电器股份有限公司 | Rotary compressor and exhaust valve |
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| CN114851322A (en) * | 2022-05-18 | 2022-08-05 | 西南林业大学 | Hot pressing method for continuous flat-pressing thick artificial board |
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| CN104100532B (en) | 2017-03-29 |
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