CN104196729A - Electric type compressor and refrigeration cycling device with electric type compressor - Google Patents
Electric type compressor and refrigeration cycling device with electric type compressor Download PDFInfo
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- CN104196729A CN104196729A CN201410453629.1A CN201410453629A CN104196729A CN 104196729 A CN104196729 A CN 104196729A CN 201410453629 A CN201410453629 A CN 201410453629A CN 104196729 A CN104196729 A CN 104196729A
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Abstract
The invention discloses an electric type compressor and a refrigeration cycling device with the electric type compressor. The electric type compressor comprises an air cylinder assembly, a piston, a main bearing, a secondary bearing and an exhausting device, wherein a central cavity and at least one peripheral cavity are arranged on the main bearing and/or the secondary bearing; the at least one peripheral cavity is arranged on the outer side of the central cavity and are communicated with the central cavity; exhausting holes are formed in one end, facing a compression cavity, of the central cavity; the exhausting device comprises exhausting valves and a limiting device; the exhausting valves are movably arranged in the central cavity to be used for enabling the exhausting holes to be opened or closed; a plurality of gas channels are defined between outer peripheral walls of the exhausting valves and an inner peripheral wall of the central cavity; and the limiting device is arranged in the central cavity and is arranged on one sides, which are away from the compression cavity, of the exhausting valves so as to limit the displacement of the exhausting valves. According to the electric type compressor disclosed by the embodiment of the invention, the area of the exhausting channels is enlarged and the loss of gas resistance is reduced, so that the efficiency of the compressor is improved.
Description
Technical field
The present invention relates to refrigerating field, especially relate to a kind of electrodynamic type compressor and there is its refrigerating circulatory device.
Background technique
As shown in Figure 11, the area of the valve accommodating groove of the tongue type outlet valve in correlation technique is large, and its bottom surface is thin, so form the bearing flange of compression chamber or the reduction of the rigidity of valve block plate, compression chamber distortion increases.Therefore, because causing compression efficiency, Leakage Gas increase reduces.Although in order to address the above problem, disclosed the free valve due to exhaust, outlet valve knee-action in correlation technique.But the aisle spare of exhaust is less, so air resistance loss increases, compressor efficiency declines.
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 electrodynamic type compressor, has increased the aisle spare of exhaust, has reduced air resistance loss.
Another object of the present invention is to propose a kind of refrigerating circulatory device with above-mentioned electrodynamic type compressor.
Electrodynamic type compressor according to the embodiment of the present invention, comprising: cylinder assembly, and described cylinder assembly comprises the cylinder with compression chamber; Piston, described piston is located in described compression chamber rotationally; Main bearing and supplementary bearing, described main bearing and described supplementary bearing are located at respectively upper-end surface and the lower end surface of described cylinder assembly, described main bearing and/or described supplementary bearing are provided with center cavity and at least one periphery chamber, described periphery chamber is located at the outside of described center cavity and is communicated with described center cavity, described center cavity towards described compression chamber one end, be provided with exhaust port; Venting gas appliance, described venting gas appliance comprises outlet valve and snubber, described outlet valve is located in described center cavity movably to open or close described exhaust port, between the periphery wall of described outlet valve and the inner circle wall of described center cavity, limit a plurality of gas channels, described snubber be located in described center cavity and the side away from described compression chamber that is positioned at described outlet valve to limit the displacement of described outlet valve.
According to the electrodynamic type compressor of the embodiment of the present invention, by being provided with a plurality of gas channels, increased the aisle spare of exhaust, reduce air resistance loss, thereby improved compressor efficiency.
In addition, electrodynamic type 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 area of described center cavity forms circle, described outlet valve comprises a plurality of even spaced juts, described in each, the periphery wall of jut and the inner circle wall of described center cavity are slidably matched, and between adjacent two described juts and the inner circle wall of described center cavity, limit a described gas channel.
In other embodiments of the present invention, the cross section of described center cavity forms regular polygon, and described outlet valve forms disc, between two limits that are often connected of described center cavity and the periphery wall of described outlet valve, limits a described gas channel.
In specific embodiments of the invention, described periphery chamber is a plurality of and circumferentially spaced apart around described center cavity.
In further embodiment of the present invention, the cross-section area that has a periphery chamber at least in described a plurality of peripheries chamber is different from the cross-section area in periphery chamber described in other, wherein, process in described piston rotation, the opening area that blocks described exhaust port and make described exhaust port when described piston rotation hour, the described periphery chamber of cross-section area maximum in described a plurality of peripheries chamber and the aperture position of described exhaust port nearest.
In a preferred embodiment of the invention, the cross-section area summation in described periphery chamber is greater than the area of described exhaust port.
According to some embodiments of the present invention, from the end away from described compression chamber of described center cavity, to the end face away from described compression chamber of described main bearing and/or described supplementary bearing, be provided with annular plane of inclination, the plane of inclination of described annular tilts to extend towards the direction at the center of center cavity on the direction from described end face to described compression chamber, and the outlet in described periphery chamber is positioned on annular plane of inclination.
According to some embodiments of the present invention, described venting gas appliance also comprises coil spring, and the two ends of described coil spring are only against between described snubber and described outlet valve often to drive exhaust port described in described exhaust valve closure.
Alternatively, described coil spring is Hookean spring or nonlinear spring.
According to the refrigerating circulatory device of the embodiment of the present invention, comprise electrodynamic type compressor according to the above embodiment of the present invention.
According to the refrigerating circulatory device of the embodiment of the present invention, by being provided with above-mentioned electrodynamic type compressor, thereby reduced air resistance loss, improved compressor efficiency.
Accompanying drawing explanation
Fig. 1 is the sectional view of rotary compressor structure portion in embodiments of the invention 1, represents the summary of venting gas appliance;
Fig. 2 is with in embodiment 1, represents the planimetric map of the valve pocket summary of the venting gas appliance that configures in main bearing flange part;
Fig. 3, with in embodiment 1, represents planimetric map and the sectional view of the details of valve pocket;
Fig. 4, with in embodiment 1, represents the component figure that completes sectional view and wherein assemble of venting gas appliance;
Fig. 5, with in embodiment 1, represents to be discharged to from compression chamber the sectional view of the gas flow of venting gas appliance;
Fig. 6, with in embodiments of the invention 2, represents to possess the outlet valve of gas channel;
Fig. 7 is with in embodiment 2, represents the planimetric map of the outlet valve assembled in valve pocket;
Fig. 8, with in embodiments of the invention 3, represents planimetric map and the sectional view of valve pocket design;
Fig. 9, with in embodiments of the invention 3, represents the sectional view of the gas flow from compression chamber to venting gas appliance exhaust;
Figure 10, with in embodiments of the invention 4, represents the planimetric map of valve pocket design;
Figure 11 is cases of design in the past, and expression possesses the planimetric map of the main bearing of tongue type valve.
Reference character:
Electrodynamic type compressor 1, housing 2, motor portion 3,
Compression mechanical part 4, cylinder 40, compression chamber 41, piston 45, eccentric shaft 60, main bearing 50, long bearing 50a, main bearing flange 50b, supplementary bearing 55, minor axis hold 55a, supplementary bearing flange 55b, exhaust silencer 51,
Venting gas appliance 10, exhaust port 13, center cavity 12, periphery chamber 16, valve pocket 11, valve seat 14, locking groove 15, slide plate 46, gas channel 16a, non-cutting portion 16b, valve seat outer circumferential face 12a, plane of inclination 18,
Outlet valve 20 (22), coil spring 35, snubber 30, jut 22a, curved part 22b.
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 10, describe in detail according to the electrodynamic type compressor 1 of the embodiment of the present invention, wherein this electrodynamic type compressor 1 comprises rotary compressor, scroll compressor and reciprocal compressor.Rotary compressor comprises compressor with rolling rotor, slide vane compressor or oscillating compressor.According to the electrodynamic type compressor 1 of the embodiment of the present invention, can be applied in refrigerating circulatory device, for example, be applied in aircondition, refrigeration plant or water heater.
Electrodynamic type compressor 1 according to the embodiment of the present invention, comprising: cylinder assembly, piston 45, main bearing 50, supplementary bearing 55 and venting gas appliance 10.Wherein, cylinder assembly comprises the cylinder 40 with compression chamber 41.When electrodynamic type compressor 1 is single cylinder compressor, cylinder assembly comprises a cylinder 40.When electrodynamic type compressor 1 is duplex cylinder compressor, cylinder assembly comprises two cylinders 40 and is located at two central diaphragms between cylinder 40.
Piston 45 is located in compression chamber 41 rotationally.Main bearing 50 and supplementary bearing 55 are located at respectively upper-end surface and the lower end surface of cylinder assembly, main bearing 50 and/or supplementary bearing 55 are provided with center cavity 12 and at least one periphery chamber 16, periphery chamber 16 is located at the outside of center cavity 12 and is communicated with center cavity 12, center cavity 12 towards compression chamber 41 one end, be provided with exhaust port 13, in center cavity 12, be also provided with annular valve seat 14, valve seat 14 arranges around exhaust port 13.Preferably, the cross-section area summation in periphery chamber 16 is greater than the area of exhaust port 13, thereby can further reduce air resistance loss.More preferably, the ratio of the cross-section area summation in periphery chamber 16 and the area of exhaust port 13 is in 1～4 scope.
Venting gas appliance 10 comprises outlet valve 20 (22) and snubber 30, outlet valve 20 is located in center cavity 12 movably to open or close exhaust port 13, between the inner circle wall of the periphery wall of outlet valve 20 and center cavity 12, limit a plurality of gas channel 16a, snubber 30 is located in center cavity 12 and is positioned at the side away from compression chamber 41 of outlet valve 20 with the displacement of restriction outlet valve 20.Particularly, outlet valve 20 is placed on valve seat 14 to be located in center cavity 12.Wherein be understandable that, when venting gas appliance 10 is located on supplementary bearing 55, the setting of outlet valve 20 should guarantee that outlet valve 20 can not drop when closing exhaust port 13.
Need to describe, electrodynamic type compressor 1 also comprises exhaust silencer 51 elements such as grade, and exhaust silencer 51 is located on main bearing 50.
Under compressed pressurized gas effect in compression chamber 41, outlet valve 20 floats to open exhaust port 13 from exhaust port 13, pressurized gas are drained in center cavity 12 by exhaust port 13, wherein the part in pressurized gas is drained in exhaust silencer 51 by gas channel 16a, and another part pressurized gas are drained in exhaust silencer 51 by periphery chamber 16.
According to the electrodynamic type compressor 1 of the embodiment of the present invention, by being provided with a plurality of gas channel 16a, increased the aisle spare of exhaust, reduce air resistance loss, thereby improved compressor efficiency.
In some embodiments of the invention, as shown in Figure 6 and Figure 7, the cross-section area of center cavity 12 forms circle, outlet valve 22 comprises a plurality of even spaced jut 22a, the inner circle wall of the periphery wall of each jut 22a and center cavity 12 is slidably matched, and between adjacent two jut 22a and the inner circle wall of center cavity 12, limits a gas channel 16a.Preferably, the number of jut 22a is 3 or 4.
In other embodiments of the present invention, the cross section of center cavity 12 forms regular polygon, and outlet valve 20 forms disc, between two limits that are often connected of center cavity 12 and the periphery wall of outlet valve 20, limits a gas channel 16a.Particularly, the contact on every limit of the periphery wall of outlet valve 20 and center cavity 12 is positioned at the central authorities of the corresponding edge of center cavity 12, the center drilling on every limit that periphery chamber 16 can center cavity 12.Preferentially, regular polygon is equilateral triangle, square, regular pentagon or regular hexagon.
According in some embodiments of the present invention, periphery chamber 16 is a plurality of and circumferentially spaced apart around center cavity 12.In the example of Fig. 3, periphery chamber 16 is 10, and in the example of Figure 10, periphery chamber 16 is 8, and wherein the number in periphery chamber 16 limits according to actual conditions, is just not specifically limited here.
As shown in Figure 8, in further embodiment of the present invention, the cross-section area that has a periphery chamber 16 at least in a plurality of peripheries chamber 16 is different from the cross-section area in other periphery chambeies 16, wherein, the process of rotating at piston 45, when piston 45 rotates the opening area that blocks exhaust port 13 and make exhaust port 13 hour, the periphery chamber 16 of the cross-section area maximum in a plurality of peripheries chamber 16 is nearest with the aperture position of exhaust port 13.In the example of Fig. 8, the cross-section area in periphery chamber 16 increases gradually by the order in periphery chamber 161,162,163,164, and the cross-section area in periphery chamber 164 is maximum.In piston 45 rotation processes, the opening area of exhaust port 13 can change, and as shown in Figure 5, now the opening area of exhaust port 13 is larger, and the gas of discharging from exhaust port 13 is assigned to a plurality of peripheries chamber 16.As shown in Figure 9, now the opening area of exhaust port 13 is less, and the gas of discharging from exhaust port 13 mainly flow into the periphery chamber 16 of cross-section area maximum, thereby guarantees that exhaust passage is larger, reduces exhaust resistance.
As shown in Fig. 1, Fig. 3-Fig. 5, Fig. 9, in some embodiments of the invention, from the end away from compression chamber 41 of center cavity 12, to the end face away from compression chamber 41 of main bearing 50 and/or supplementary bearing 55, be provided with annular plane of inclination 18, the plane of inclination 18 of annular tilts to extend towards the direction at center cavity 12 center in 41 direction from end face to compression chamber, and the outlet in periphery chamber 16 is positioned on annular plane of inclination 18.Thereby by being provided with annular plane of inclination 18, can increase the opening area in each periphery chamber 16, the air-flow of mitigation from periphery chamber 16 to exhaust silencer 51, therefore not only can reduce the drag losses of exhaust gas, the noise producing in the time of also can reducing exhaust silencer 51 jet exhaust gas.
In some embodiments of the invention, as shown in Figure 4 and Figure 5, venting gas appliance 10 also comprises coil spring 35, and the two ends of coil spring 35 are only against between snubber 30 and outlet valve 20 often to drive outlet valve 20 to close exhaust port 13.Thereby by being provided with coil spring 35, can relax waving of outlet valve 20.Alternatively, coil spring 35 is Hookean spring or nonlinear spring.
According to the refrigerating circulatory device of the embodiment of the present invention, comprise electrodynamic type compressor 1 according to the above embodiment of the present invention, thereby reduced air resistance loss, improved compressor efficiency.
The electrodynamic type compressor of four specific embodiments according to the present invention is described below with reference to Fig. 1-Figure 11.
Embodiment 1:
Embodiment 1 is the case that venting gas appliance of the present invention adopts on rotary compressor.The design's form is general in comprising the motor compressor of rotary compressor.
In Fig. 1, rotary compressor 1 consists of the motor portion 3 that is fixed on compression mechanical part 4 on housing 2 internal diameters, its top configuration.Compression mechanical part 4 possesses: in the compression chamber 41 forming in cylinder 40, this cylinder, carry out eccentric operating piston 45, with the reciprocating slide plate of this piston synchronous (without diagram), to piston 45 carry out the eccentric shaft 60 of eccentric drive, to 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 and supplementary bearing flange 55b forms respectively.Main bearing flange 50b and supplementary bearing flange 55b are fixed in cylinder 40, have formed the compression chamber 41 of sealing together with cylinder 40.Venting gas appliance 10, can be configured in the one side or both of main bearing flange 50b or supplementary bearing flange 55b, embodiment 1 has configured venting gas appliance 10 in main bearing flange 50b, exhaust silencer 51 has been installed on its top.
In compression chamber 41, the pressurized gas of compression, by the exhaust port 13 to compression chamber 41 openings, are diverted to being discharged in exhaust silencer 51 in the periphery chamber 16 of center cavity 12 openings.From outlet pipe (without diagram) to refrigeration plant discharge thereafter.Therefore, the internal pressure of housing 2 is high pressure.
Before explanation venting gas appliance 10, first, the component parts of venting gas appliance 10 is described.
Fig. 2 is the planimetric map of the main bearing flange 50b after processing.The valve pocket 11 possessing in main bearing flange 50b, in the bottom centre of center cavity 12, along 10 periphery chambeies 16 of the interior week configuration of exhaust port 13, valve seat 14, center cavity 12 with by the inclined-plane that the upper end open face in these center cavities 12 and periphery chamber 16 carries out conical chamfer machining, form.In addition, in center cavity 12, possessed circular locking groove 15 (shown in Fig. 3).
At this, center cavity 12 and periphery chamber 16 are cylinder type, as described later, also passable even if the sectional shape of center cavity 12 is regular polygon.In addition, periphery chamber 16 is that gas channel is just passable, not necessarily cylindrical.As a reference, Fig. 2 represents at the internal diameter of compression chamber 41 and the dotted line for position (---) of slide plate 46.
Fig. 3 is planimetric map and the sectional view (X-X cross section) thereof of valve pocket 11.Be configured in the outside of center cavity 12 10 periphery chambeies 16, possess the gas channel 16a to interior all openings of center cavity 12 separately.Gas channel 16a is the exhaust passage from the pressurized gas of exhaust port 13 discharges.On the other hand, 10 non-cutting portion 16b that surrounded by gas channel 16a separately and center cavity 12 have just formed.The locking groove possessing in interior week 15 at center cavity 12 is to insert the fixedly circumferential groove of snubber 30 (Fig. 4).
The volume of exhaust port 13 is exhaust clearance volume, and wherein residual pressurized gas become expansion-loss again.Therefore, the height of exhaust port 13 is necessary to reduce.Due to the design's requirement, the thinnest at the wall thickness (C) of valve seat 14 and the valve seat outer circumferential face 12a that forms between the interior week of center cavity 12, be generally 1.5～2.0mm.
The present invention uses in valve pocket 11 the free valve without fixing part, so that the area of plane of valve seat outer circumferential face 12a is compared with the venting gas appliance that uses tongue type valve is in the past little a lot.And, the surrounding of valve seat outer circumferential face 12a by non-cutting portion 16b around, strengthen to some extent.That is, around the total measurement (volume) of the non-cutting portion 16b of valve pocket 11, basic with from plane of inclination, 18 to deduct the volume in periphery chamber 16 suitable.
Like this, use the valve pocket 11 of free valve still not small-sized, and formed with together with the configuration in periphery chamber 16 rigidity that non-cutting portion 16b has strengthened valve pocket 11, this is also one of object of the present invention.That is, by possessing the rigidity of the main bearing flange 50b of valve pocket 11, promote, improved the internal modification of compression chamber 11.And the noise that promotes exhaust port 13 and outlet valve 20 (Fig. 4) generation by rigidity can reduce.At this, plane of inclination 18 can reduce the passage long (groove depth in periphery chamber) in periphery chamber 16, the pressure loss of reduction exhaust.But the thinner thickness of main bearing flange 50b, also can omit plane of inclination 18.
The venting gas appliance 10 and these general assembly components that in Fig. 4, expression main bearing flange 50b, complete.General assembly component is outlet valve 20, coil spring 35, snubber 30 from lower beginning in order.Outlet valve 20 is that thickness of slab is the plectane of 0.2～0.3mm left and right.Between the external diameter of outlet valve 20 and the internal diameter of center cavity 12, only has very little gap, such as the glade plane space of 20～200 about μ m, so the centre of center cavity 12 knee-action sleekly.
Coil spring 35 is that wire diameter is the Compress Spring of 0.2～0.5mm, and cylinder, circular cone, contrary circular cone, cydariform etc. are more applicable.In addition, except line style spring, also use non-linear spring, with the unsteady direct ratio that grows up to of center cavity 12, increase spring constant and be also highly profitable.Snubber 30 is the central C shape jump ring that has opening portion.In addition, as snubber, also can use thin lining nut etc.Coil spring 35 and snubber 30 can have various designs according to purport of the present invention in addition, so need not be limited in the scope of above-mentioned explanation.
As a reference, the cases of design of the rotary compressor carrying in domestic air conditioner (1HP) is described.The external diameter of the internal diameter of center cavity 12 and outlet valve 20 is that the internal diameter of 13～15mm, exhaust port 13 is that the maximum compression of 8～10mm, coil spring 35 is that the path increment (knee-action width) of 0.3～1.0N, outlet valve 20 is 2～3mm.
These data, can be used as a case, just in order to be easier to understand disclosure of the present invention, are not to be limited in above-mentioned scope.In addition, in duplex cylinder compressor, the air displacement of 1 cylinder can reduce, so each numerical value can reduce.In addition, in the high refrigeration plant of compression ratio, outlet valve path increment can reduce, so coil spring can omit.
Fig. 5 is the sectional view of compression mechanical part 4, represents the venting gas appliance 10 possessing in compression chamber 41 and main bearing flange 50b.According to Fig. 5, the mobile of exhaust airstream described.Because compressed pressurized gas in compression chamber 41 make outlet valve 20 from valve seat 14 floatings.Pressurized gas, by this floating gap, are diverted in 10 periphery chambeies 16 and rise, and from plane of inclination 18, are out discharged to exhaust silencer 51 (Fig. 1).In this exhaust stroke, the opening area that plane of inclination 18 expands each periphery chamber 16, relaxes the air-flow from periphery chamber 16 to exhaust silencer 51.Therefore, the drag losses of exhaust gas still can not reduced in plane of inclination 18, can reduce the noise producing when exhaust silencer 51 is sprayed yet.
At this, the gap (S) forming between the outlet valve 20 of floating and valve seat 14 is valve block stroke.Valve block stroke is long maximum, and coil spring 35 is also pressed the most tightly, and outlet valve 20 is stopping in a flash, if air displacement reduces, outlet valve 20 can reduce Valve travel amount to be got back on valve seat 14.
In above-mentioned exhaust stroke, outlet valve 20 is along with waving knee-action.This waves excessive, and the closing velocity of valve seat 14 can slow down, thus from the adverse current of 11 pairs of compression chambers 41 of valve pocket, can cause refrigerating capacity to decline, and also power consumption can increase.Particularly, the operating conditions that air displacement is many, gives one example, and motor speed, when 100rps is above, will easily produce above-mentioned phenomenon.
The effect of coil spring 35 is to relax waving of outlet valve 20.The active force of coil spring 35 increases, and is reduced to direct ratio with the path increment (S) of outlet valve 20, and waving of outlet valve 20 can reduce.But above-mentioned means can increase exhaust resistance, so according to the characteristic of application apparatus, need to consider the design of the path increment (S) of coil spring 35 and outlet valve 20.
Next, the cases of design in periphery chamber 16 is described.In the cases of design of above-mentioned domestic air conditioner, the internal diameter in periphery chamber 16 (D1) is that the ratio (R) that 4mm, its quantity (n) are 10, the internal diameter (D2) of exhaust port 13 is 9mm, the total sectional area (A1) in periphery chamber 16 and the aisle spare (A2) of exhaust port 13 is R=A1/A2=(4/9)
2the total sectional area in xn=1.97, periphery chamber 16 (A2) is about 2 times of aisle spare (A1) of exhaust port 13.But consideration should be about 1.0～4.0 scope to the more air-conditioning of air displacement, use refrigerant and the words of motor rotational speed, above-mentioned R from the few cryogenic device of extraction flow.
Next, the manufacture method of venting gas appliance 10 is carried out to simple explanation.In Fig. 3, during processing valve pocket 11, adopt the multiple-spindle milling machine processing such as 2 axles or 3 axles, several peripheries chamber is processed simultaneously.With center cavity together with, by the order of exhaust port 13 and valve seat 14 and plane of inclination 18 process thereafter.Finally, at the interior cycle deburring of center cavity 12.Packaging technology is very simple, can carry out automation.Like this, adopt the valve pocket of circle formation and the phone tool easy processing of component.In addition, valve pocket 11 carries out moulding by sintered alloy or forging method, can significantly omit above-mentioned machining.
Embodiment 2:
The words that the design that the internal diameter of exhaust port 13 is less or the internal diameter of center cavity 12 expand a little, and the valve seat outer circumferential face 12a forming between valve seat 14 slightly makes the words that expand, the valve seat outer circumferential face 12a forming between the periphery of outlet valve and valve seat 14 can become greatly, so the outer circumferential side of outlet valve can append gas channel.
Dull and stereotyped outlet valve 22 shown in Fig. 6, by 4 jut 22a that uniformly-spaced configure and curved part 22b, formed.4 jut 22a are curves on circle, more a little bit smaller than the internal diameter of center cavity 12.The width of jut 22a (W1) is larger than the width (W2) of the gas channel 16a in periphery chamber 16 in addition.So jut 22a can not be embedded in gas channel 16a inside, outlet valve 22 can slide up and down swimmingly.
Fig. 7 can assemble the planimetric map of outlet valve 22 in valve pocket 11.4 curved part 22b, be and center cavity 12 between the passage of the exhaust of appending.In addition, thus W1 > W2 jut 22a can not be embedded in gas channel 16a.In addition, the quantitative aspects 3～4 of jut 22a or curved part 22b is more favourable, and the quantity of jut 22a increases, and the general passage area of curved part 22b can reduce.
The pressurized gas of discharging from exhaust port 13, in flowing to 10 periphery chambeies 16 in, be diverted in 4 curved part 22b, from center cavity 12, be out discharged to exhaust silencer 51.At this, collaborate with the exhaust that flow out in periphery chamber 16.And there is large gas channel at snubber 30 center, so also can reduce from curved part 22b exhaust resistance out.
In addition, by appending curved part 22b, the area of outlet valve 22 will reduce, so the active force of the exhaust of the directive effect floating to outlet valve 22 can reduce.Its result, curved part 22b still can not reduce drag losses, and also has the effect of further stablizing outlet valve 22 postures.
In addition, the lower end of curved part 22b coil spring 35 is heavy, so the useful area of curved part 22b may diminish, but wire diameter is below 0.5mm, so do not worry that the useful area of curved part 22b can significantly reduce.In addition, use contrary cone type coil spring, at the little end face of wire diameter, the core of outlet valve 22 is exerted pressure, the useful area of curved part 22b has not just had any problem.
Embodiment 3:
Rotary compressor is due to the revolution of piston 45, and the effective vent area of exhaust port 13 can significantly change.Such as, the angle of swing of piston 45, from slide plate center, starting is 150 while spending, the opening area maximum (100%) of exhaust port 13, thereafter, and towards the direction of 360 degree, useful area reduces, the opening area minimum (approximately 15%) before and after about 355 degree.
This phenomenon, is also appreciated that by Fig. 5.Because the piston 45 revolving round the sun in compression chamber 41 can change the opening area of exhaust port 13, its aperture position is partial to the peripheral direction of exhaust port 13, so the air-flow of discharging from exhaust port 13 is to the direction set of skew.
The internal diameter in periphery chamber in Fig. 8, separately or gas channel increase gradually by the order in periphery chamber 161,162,163,164.Therefore, the position consistency in the offset direction of the effective vent of exhaust port 13 and periphery chamber 164.Fig. 9 is the sectional view of compression chamber 41 and venting gas appliance 10.The rotational position of piston 45 is approximately 350 degree, when dwindling the effective vent area of exhaust port 13, its aperture position is towards the direction skew in periphery chamber 164.
The gas of discharging from exhaust port 13,164 flows out from the aperture position of exhaust port 13 to immediate periphery chamber, in addition, can be to periphery chamber 163 and 162 shuntings.Therefore waving of outlet valve 20, not only can reduce exhaust resistance, can also average the distribution of the active force of the planar surface portion of outlet valve 20, so can reduce.Like this, embodiment 3 feature is to the gas passage area in individual periphery chamber 16, to be optimized respectively.
Embodiment 4:
The feature of embodiment 4 shown in Figure 10 is just polygonal by the sectional shape of its center cavity 12 is made, and between center cavity 12 and the outlet valve 20 of circle, has appended gas channel 12d.In addition, for the consideration to manufacturing, 4 interior angles are R shape.
The same with other embodiment, in the bottom surface of center cavity 12, possessed exhaust port 13 and valve seat 14.8 the periphery chambeies that configured in interior week along center cavity 12.But notice that periphery chamber 16 is not to forming the central opening on 4 limits of center cavity 12.The external diameter of the outlet valve 20 possessing in center cavity 12, has gap, than the width of center cavity 12 is smaller, can slide.
The contact in the interior week of the periphery of outlet valve 20 and center cavity 12, must be the central authorities on 4 limits of square.The action of the substantially horizontal by these four contact outlet valves 20 is restricted, and can only carry out the action of above-below direction.Above-mentioned contact is the slip surface of outlet valve 20 line contacts, so slip resistance is little, advantage is stably knee-action of outlet valve 20.And circular outlet valve 20 can rotation, so outlet valve 20 can not produce local abrasion.In addition, this slip surface, as mentioned above, the configuration by the periphery chamber 16 considered in advance can form non-cutting portion 16b.
The combination of embodiment 4, the center cavity 12 by square and circular outlet valve 20, appends 4 gas channel 12d, forms the effect of 4 good slip surfaces.In addition, by appending 4 gas channel 12d, can improve the balance of the gas load that makes outlet valve 20 floatings.In addition, in Figure 10, in the restraining groove 15 (without figure) that the central authorities on 4 limits of snubber 30 (without diagram) embedding possess.In addition, coil spring 35 does not illustrate yet.
At this, the sectional shape of center cavity 12 is to comprise that the regular polygon of square is just passable.But if the quantity on polygonal limit increases, the quantity of gas channel 12d can increase, but the gross area of gas channel 12d can reduce, so not good scheme.Therefore, center cavity 12 is that scope from equilateral triangle to regular hexagon is practical.And from the viewpoint of manufacturing, the processability of square is superior.But, use the sintered alloy method of forming, manufacturing aspect does not have difference.
Below summary of the present invention and effect are described.
(1) venting gas appliance of the present invention, be the periphery of the center cavity of circular row air valve knee-action be configured as several gas channels periphery chamber, improving the rigidity of venting gas appliance in, realize miniaturization (embodiment 1).In outlet valve, append gas channel, reduce air resistance (embodiment 2).And, respectively the size in periphery chamber is optimized, reduce air resistance (embodiment 3).By making the square that is shaped as of center cavity, append 4 gas channels, form round and smooth outlet valve slip surface (embodiment 4).
(2) by these ways and effect, reduce exhaust port air resistance loss out, and the action of further stablizing outlet valve, improve compression efficiency.Can improve noise in addition.
(3) because number of components is less, so assembling performance is superior.Processing and moulding are also very superior in addition.
(4), due to above-mentioned feature, the outlet valve that the present invention can be used as electrodynamic type compressor extensively adopts.
In industry, utilize possibility
The motor compressor that comprises rotary compressor of the present invention can use in air conditioner, refrigeration plant, water heater etc., and in addition, the present invention also can use in the rotary compressor of housing low pressure.Venting gas appliance of the present invention is easy to manufacture.
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. an electrodynamic type compressor, is characterized in that, comprising:
Cylinder assembly, described cylinder assembly comprises the cylinder with compression chamber;
Piston, described piston is located in described compression chamber rotationally;
Main bearing and supplementary bearing, described main bearing and described supplementary bearing are located at respectively upper-end surface and the lower end surface of described cylinder assembly, described main bearing and/or described supplementary bearing are provided with center cavity and at least one periphery chamber, described periphery chamber is located at the outside of described center cavity and is communicated with described center cavity, described center cavity towards described compression chamber one end, be provided with exhaust port;
Venting gas appliance, described venting gas appliance comprises outlet valve and snubber, described outlet valve is located in described center cavity movably to open or close described exhaust port, between the periphery wall of described outlet valve and the inner circle wall of described center cavity, limit a plurality of gas channels, described snubber be located in described center cavity and the side away from described compression chamber that is positioned at described outlet valve to limit the displacement of described outlet valve.
2. electrodynamic type compressor according to claim 1, it is characterized in that, the cross-section area of described center cavity forms circle, described outlet valve comprises a plurality of even spaced juts, described in each, the periphery wall of jut and the inner circle wall of described center cavity are slidably matched, and between adjacent two described juts and the inner circle wall of described center cavity, limit a described gas channel.
3. electrodynamic type compressor according to claim 1, it is characterized in that, the cross section of described center cavity forms regular polygon, and described outlet valve forms disc, between two limits that are often connected of described center cavity and the periphery wall of described outlet valve, limits a described gas channel.
4. electrodynamic type compressor according to claim 1, is characterized in that, described periphery chamber is a plurality of and circumferentially spaced apart around described center cavity.
5. electrodynamic type compressor according to claim 4, it is characterized in that, the cross-section area that has a periphery chamber at least in described a plurality of peripheries chamber is different from the cross-section area in periphery chamber described in other, wherein, process in described piston rotation, the opening area that blocks described exhaust port and make described exhaust port when described piston rotation hour, the described periphery chamber of cross-section area maximum in described a plurality of peripheries chamber and the aperture position of described exhaust port nearest.
6. electrodynamic type compressor according to claim 1, is characterized in that, the cross-section area summation in described periphery chamber is greater than the area of described exhaust port.
7. electrodynamic type compressor according to claim 1, it is characterized in that, from the end away from described compression chamber of described center cavity, to the end face away from described compression chamber of described main bearing and/or described supplementary bearing, be provided with annular plane of inclination, the plane of inclination of described annular tilts to extend towards the direction at the center of center cavity on the direction from described end face to described compression chamber, and the outlet in described periphery chamber is positioned on annular plane of inclination.
8. electrodynamic type compressor according to claim 1, is characterized in that, described venting gas appliance also comprises coil spring, and the two ends of described coil spring are only against between described snubber and described outlet valve often to drive exhaust port described in described exhaust valve closure.
9. electrodynamic type compressor according to claim 8, is characterized in that, described coil spring is Hookean spring or nonlinear spring.
10. a refrigerating circulatory device, is characterized in that, comprises according to the electrodynamic type compressor described in any one in claim 1-9.
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| CN201410453629.1A CN104196729B (en) | 2014-09-05 | 2014-09-05 | Electrodynamic type compressor and the refrigerating circulatory device with it |
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| CN201410453629.1A CN104196729B (en) | 2014-09-05 | 2014-09-05 | Electrodynamic type compressor and the refrigerating circulatory device with it |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4510098B2 (en) * | 2008-01-07 | 2010-07-21 | 日立アプライアンス株式会社 | Scroll compressor |
| CN102094823A (en) * | 2009-12-10 | 2011-06-15 | 广东美芝制冷设备有限公司 | Cylinder assembly and core-adjusting method for cylinder of double-cylinder rotary compressor |
| CN102235360A (en) * | 2010-05-07 | 2011-11-09 | 广东美芝制冷设备有限公司 | Double-cylinder rotary compressor |
| WO2012102322A1 (en) * | 2011-01-28 | 2012-08-02 | 三菱重工業株式会社 | Electric compressor and assembly method therefor |
| CN103410734A (en) * | 2013-08-02 | 2013-11-27 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN204140432U (en) * | 2014-09-05 | 2015-02-04 | 广东美芝制冷设备有限公司 | Electrodynamic type compressor and there is its refrigerating circulatory device |
-
2014
- 2014-09-05 CN CN201410453629.1A patent/CN104196729B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4510098B2 (en) * | 2008-01-07 | 2010-07-21 | 日立アプライアンス株式会社 | Scroll compressor |
| CN102094823A (en) * | 2009-12-10 | 2011-06-15 | 广东美芝制冷设备有限公司 | Cylinder assembly and core-adjusting method for cylinder of double-cylinder rotary compressor |
| CN102235360A (en) * | 2010-05-07 | 2011-11-09 | 广东美芝制冷设备有限公司 | Double-cylinder rotary compressor |
| WO2012102322A1 (en) * | 2011-01-28 | 2012-08-02 | 三菱重工業株式会社 | Electric compressor and assembly method therefor |
| CN103410734A (en) * | 2013-08-02 | 2013-11-27 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN204140432U (en) * | 2014-09-05 | 2015-02-04 | 广东美芝制冷设备有限公司 | Electrodynamic type compressor and there is its refrigerating circulatory device |
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| CN104196729B (en) | 2017-10-03 |
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