CN103437999A - Rotary compressor and air conditioner with same - Google Patents
Rotary compressor and air conditioner with same Download PDFInfo
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- CN103437999A CN103437999A CN2013103658009A CN201310365800A CN103437999A CN 103437999 A CN103437999 A CN 103437999A CN 2013103658009 A CN2013103658009 A CN 2013103658009A CN 201310365800 A CN201310365800 A CN 201310365800A CN 103437999 A CN103437999 A CN 103437999A
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Abstract
The invention discloses a rotary compressor and an air conditioner with the same. The rotary compressor comprises a housing, a driver, an air cylinder, a main bearing, an auxiliary bearing, a crankshaft, a first slip sheet and a second slip sheet, wherein the driver is arranged in the housing; the air cylinder is arranged in the housing; a first slip sheet groove and a second slip sheet groove are formed in the air cylinder; the main bearing and the auxiliary bearing are arranged at the top and the bottom of the air cylinder respectively and define a chamber along with the air cylinder; the crankshaft is driven by the driver to rotate and penetrates through the main bearing and the auxiliary bearing; a piston is eccentrically sleeved on the crankshaft; the piston is rotatable relative to the crankshaft; the first slip sheet and the second slip sheet are movably arranged in the first slip sheet groove and the second slip sheet groove respectively; the inner end of the first slip sheet extends into the chamber and is connected with the piston to enable the first slip sheet to swing at a predefined angle alpha which is not smaller than -1.1*atan (e/R) and not greater than 1.1*atan (e/R); the inner end of the second slip sheet is separably matched with the outer circumferential surface of the piston. According to the rotary compressor, the efficiency of the rotary compressor is improved.
Description
Technical field
The present invention relates to art of refrigeration units, especially relate to a kind of rotary compressor and the air conditioner with it.
Background technique
In recent years, the method that the rotating speed that changes motor by converter technique is controlled the air-conditioning ability and improved energy efficiency is popularized.But the method has increased the quantity of electronic component, brings integrity problem, and the shortcoming of cost up.
Traditional twin-tub variable capacity rotation compressor is that the working state by controlling any one cylinder realizes transfiguration.In this twin-tub variable capacity rotation compressor, when two cylinders, work simultaneously, carry out compression, be high ability mode; The compression of interrupting in any one cylinder wherein reduces compression work, is low ability mode.Yet this twin-tub variable capacity rotation compressor is compared with the single cylinder rotary compressor, there is the many and high shortcoming of fabricating cost of the quantity of component, and, owing to having increased a set of compression assembly, increased friction pair, make the frictional loss increase.
Summary of the invention
The present invention is intended at least solve one of technical problem existed in prior art.For this reason, one object of the present invention is to propose the rotary compressor that a kind of frictional loss is little and cost is low.
Another object of the present invention is to propose a kind of air conditioner with above-mentioned rotary compressor.
Rotary compressor according to first aspect present invention embodiment comprises: housing; Driver, described driver is located in described housing; Cylinder, described cylinder is located in described housing and on described cylinder and is formed with the first vane slot and the second vane slot; Main bearing and supplementary bearing, described main bearing and supplementary bearing are located at respectively top and the bottom of described cylinder and jointly limit chamber with described cylinder; Bent axle, described bent axle is rotated and is run through described main bearing and described supplementary bearing by described driver drives, is arranged with prejudicially piston on described bent axle, and described piston is rotatable with respect to described bent axle; With the first slide plate and the second slide plate, described the first slide plate and described the second slide plate are located at respectively in described the first vane slot and described the second vane slot movably, and the inner of described the first slide plate extend in described chamber and is connected with described piston, so that described the first slide plate swings in predetermined angle, and-1.1 * atan(e/R)≤α≤1.1 * atan(e/R), the inner of described the second slide plate coordinates separably with the outer circumferential face of described piston, the offset that wherein e is described bent axle, the radius that R is described cylinder.
According to the rotary compressor of the embodiment of the present invention, by the inner by the first slide plate, with piston, be connected so that the first slide plate swings in predetermined angle, effectively reduced frictional loss and leakage between the first slide plate and piston, improved the efficiency of rotary compressor.In addition, the volume of this rotary compressor is little, component are few and cost is low.
In addition, also can there is following additional technical feature according to rotary compressor of the present invention:
According to one embodiment of present invention, on described piston, be formed with reentrant part, the inner of described the first slide plate is provided with lug boss, and described lug boss coordinates that with the female section described the first slide plate is connected to described piston pivotly.Thus, by lug boss and reentrant part are set, effectively reduced on the one hand the speed of related movement of piston and the first slide plate, reduced the sliding friction loss of piston and the first slide plate, increase on the other hand the area of contact between piston and the first slide plate, reduced end leakage.
Further, described rotary compressor further comprises: two swing lining, be formed with respectively curve bath on the opposing sidewalls of described the first vane slot, described two swing linings are contained in two described curve baths rotationally, and described the first slide plate is located at movably described two and swings between linings.Thus, by the swing lining is set, the first slide plate can swing along with the motion of piston better.
According to one embodiment of present invention, described piston is provided with lug boss, and the inner of described the first slide plate is formed with reentrant part, and the female section coordinates that with described lug boss described the first slide plate is connected to described piston pivotly.
According to another embodiment of the invention, described the first slide plate and described piston are one-body molded, and described the first slide plate swings linings pivotly in described the first vane slot and swing between linings removable at described two by two.Thus, by arranging two, swing linings, when bent axle drives piston and moves along the inwall of chamber, piston can drive the first slide plate along the first vane slot move axially and around two axis oscillatings that swing linings.
According to one embodiment of present invention, the inner of the second slide plate coordinates by the pressure switching mechanism separably with the outer circumferential face of piston, and described pressure switching mechanism is switched the pressure in described the second vane slot between low-pressure lateral pressure and high side pressure.Thus, by the pressure switching mechanism is set, the pressure in the second vane slot can be switched between low-pressure lateral pressure and high side pressure.
Alternatively, described pressure switching mechanism is three-way valve, and described three-way valve has the first to the 3rd valve port, and described the first valve port communicates with described the second vane slot, described the second valve port communicates with described enclosure interior, and described the 3rd valve port communicates with the liquid-storage container of described rotary compressor.
According to one embodiment of present invention, the angle between the center line of the center line of described the first vane slot and described the second vane slot is 30 °～330 °.
Alternatively, the angle between the center line of the center line of described the first vane slot and described the second vane slot is 180 °.
Alternatively, described driver is variable-frequency motor.
According to second aspect present invention embodiment's air conditioner, comprise the rotary compressor of the above-mentioned first aspect embodiment according to the present invention.
According to one embodiment of present invention, the described housing of described rotary compressor is provided with the pressure switching pipe communicated with described the second vane slot, and an end of described pressure switching pipe is located between the outdoor heat exchanger of the four-way valve of described air conditioner and described air conditioner.
Additional aspect of the present invention and advantage part in the following description provide, and part will become obviously from the following description, or recognize by practice of the present invention.
The accompanying drawing explanation
Above-mentioned and/or additional aspect of the present invention and advantage are from obviously and easily understanding becoming embodiment's description in conjunction with following accompanying drawing, wherein:
Fig. 1 is the schematic diagram of air conditioner according to an embodiment of the invention;
Fig. 2 a is the plan view of rotary compressor according to an embodiment of the invention;
Fig. 2 b is the plan view of rotary compressor in accordance with another embodiment of the present invention;
Fig. 2 c is the plan view of another embodiment's the rotary compressor according to the present invention;
Fig. 3 is the schematic diagram of the air conditioner that is low-pressure lateral pressure of the pressure in the second vane slot of rotary compressor according to an embodiment of the invention;
Fig. 4 a-Fig. 4 d is the working procedure schematic diagram of the rotary compressor shown in Fig. 3;
Fig. 5 is the schematic diagram of the air conditioner that is high side pressure of the pressure in the second vane slot of rotary compressor according to an embodiment of the invention;
Fig. 6 a-Fig. 6 d is the working procedure schematic diagram of the rotary compressor shown in Fig. 5;
Fig. 7 is the performance plot of rotary compressor according to an embodiment of the invention;
Fig. 8 is the schematic diagram of air conditioner in accordance with another embodiment of the present invention.
Description of reference numerals:
100: rotary compressor;
1: housing; 11: outlet pipe; 12: pressure switching pipe;
21: stator; 22: rotor;
3: cylinder; 31: the first vane slots; 311: the first slide plates; 3111: lug boss;
312: swing lining;
32: the second vane slots; 321: the second slide plates; 33: intakeport;
4: main bearing; 41: the first row gas port; 42: the second row gas port;
5: supplementary bearing; 6: bent axle; 7: piston; 71: reentrant part;
8: the pressure switching mechanism; 81: the first valve ports; 82: the second valve ports; 83: the three valve ports;
9: liquid-storage container; 91: suction tude; 92: steam outlet pipe;
200: air conditioner;
201: outdoor heat exchanger; 202: throttling arrangement;
203: indoor heat exchanger; 204: four-way valve;
O point: the center of cylinder; O1 point: the center of piston;
O2 point: the center of rotation that swings lining;
α angle: the first slide plate pivot angle, the angle of the line that the line that O1 point and O2 are ordered and O point and O1 are ordered.
Embodiment
Below describe embodiments of the invention in detail, described embodiment's example is shown in the drawings, and wherein same or similar label means same or similar element or the element with identical or similar functions from start to finish.Be exemplary below by the embodiment who is described with reference to the drawings, only 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, orientation or the position relationship of the indications such as term " " center ", " laterally ", " on ", D score, " left side ", " right side ", " vertically ", " level ", " top ", " end ", " interior ", " outward " be based on orientation shown in the drawings or position relationship; be only the present invention for convenience of description and simplified characterization; rather than the device of indication or hint indication or element must have specific orientation, with specific orientation structure and operation, so can not be interpreted as limitation of the present invention.In addition, term " first ", " second " be only for describing purpose, 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, except as otherwise noted, the implication of " a plurality of " is two or more.
In description of the invention, it should be noted that, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection " should be done broad understanding, for example, can be to be fixedly connected with, and can be also to removably connect, or connect integratedly; Can be mechanical connection, can be also to be electrically connected to; Can be directly to be connected, also can indirectly be connected by intermediary, can be the connection of two element internals.For the ordinary skill in the art, can concrete condition understand above-mentioned term concrete meaning in the present invention.
Below with reference to Fig. 1-Fig. 8, the rotary compressor 100 according to the embodiment of the present invention is described.
As shown in Figure 1, according to first aspect present invention embodiment's rotary compressor 100, comprise housing 1, driver, cylinder 3, main bearing 4, supplementary bearing 5, bent axle 6, the first slide plate 311 and the second slide plate 321.
Driver is located in housing 1.Cylinder 3 is located in housing 1, and is formed with the first vane slot 31 and the second vane slot 32 on cylinder 3.For example, in the example of Fig. 1, limit holding space in housing 1, driver is located at the top of holding space, cylinder 3 is located at the bottom of holding space and is positioned at the below of driver, cylinder 3 can form all unlimited cylindrical shapes of top and bottom, is formed with the first vane slot 31 and the second vane slot 32 that radially extend and be spaced apart from each other on the sidewall of cylinder 3.Alternatively, driver is motor.
Main bearing 4 and supplementary bearing 5 are located at respectively top and the bottom of cylinder 3, and main bearing 4, supplementary bearing 5 and cylinder 3 limit chamber jointly.That is to say, main bearing 4 is located at the top of cylinder 3, and supplementary bearing 5 is located at the bottom of cylinder 3, and main bearing 4, supplementary bearing 5 and cylinder 3 these threes limit chamber jointly.
Bent axle 6 is rotated by driver drives, and bent axle 6 and run through main bearing 4 and supplementary bearing 5 is arranged with piston 7 prejudicially on bent axle 6, and piston 7 is rotatable with respect to bent axle 6.With reference to Fig. 1, bent axle 6 extends and along the vertical direction successively through main bearing 4, chamber and supplementary bearing 5, bent axle 6 is provided with eccentric part, eccentric part is contained in chamber, and alternatively, eccentric part and bent axle 6 are one-body molded, piston 7 is set in outside eccentric part, when rotary compressor 100 work, the driver for example eccentric part on motor driving crank 6 is made eccentric rotary, thereby drive piston 7, along the inwall of chamber, moves.
The first slide plate 311 and the second slide plate 321 are located at respectively in the first vane slot 31 and the second vane slot 32 movably.That is to say, as shown in Fig. 1-Fig. 6, the first slide plate 311 is located in the first vane slot 31 movably, and the second slide plate 321 is located in the second vane slot 32 movably.
The inner of the first slide plate 311 extend in chamber, and the inner of the first slide plate 311 (example is lower end as shown in Figure 2) be connected with piston 7, so that the first slide plate 311 swings in predetermined angle.Now, the inner of the first slide plate 311 (example is lower end as shown in Figure 2) can be along with the motion of piston 7 in the interior movement of the first vane slot 31, and swings in certain angular range, as shown in Figure 2 c, the first slide plate 311 swings in predetermined angle, and wherein, α is configured to:
-1.1×atan（e/R）≤α≤1.1×atan（e/R）
Wherein, the offset that e is bent axle 6, the radius that R is cylinder 3.Particularly, with reference to Fig. 2 c, predetermined angle is the angle between O1 point and the O2 line of ordering and O point and the O1 line of ordering, wherein, the center that the O point is cylinder 3, the center that the O1 point is piston, the oscillation center that the O2 point is the first slide plate 311, the distance between O point and O1 point is the eccentric amount e of bent axle 6.Here, it should be noted that, " being connected " should make broad understanding here, and for example the inner of the first slide plate 311 is connected pivotly with piston 7, or be fixedly linked etc.In addition, " the inner " can be understood as the end towards the chamber center, and its contrary end is defined as " outer end ", away from the end at chamber center.
The inner of the second slide plate 321 (example is upper end as shown in Figure 2) coordinates separably with the outer circumferential face of piston 7.For example rotary compressor 100 is under high ability mode M, the inner of the second slide plate 321 (example is upper end as shown in Figure 2) is spaced apart from each other with the outer circumferential face of piston 7, now the second slide plate 321 is accommodated in the second vane slot 32, rotary compressor 100 is under low ability mode N, the inner of the second vane slot 32 extend in chamber and only supports piston 7, by controlling the action of the second slide plate 321, can change the discharge capacity of rotary compressor 100, thereby improve the performance of air conditioner 200 like this.
Further, be formed with intakeport 33, first row gas port 41 and second row gas port 42 on one of them in cylinder 3, main bearing 4 and supplementary bearing 5.In other words, intakeport 33, first row gas port 41 and second row gas port 42 all can be formed on cylinder 3, main bearing 4 or supplementary bearing 5.Alternatively, intakeport 33 is formed on cylinder 3, and first row gas port 41 and second row gas port 42 are formed on main bearing 4.Wherein the contiguous intakeport 33 of the first vane slot 31 arranges, and first row gas port 41 and second row gas port 42 are respectively adjacent to the first vane slot 31 and the second vane slot 32 arranges.For example first row gas port 41 is positioned at the upstream side of the first vane slot 31 on the sense of rotation of bent axle 6, and second row gas port 42 is positioned at the upstream side of the second vane slot 32 on the sense of rotation of bent axle 6.Here, it should be noted that, " upstream " can be understood as the upstream of the flow direction of refrigerant in chamber.
In one embodiment of the invention, the inner that is formed with reentrant part 71, the first slide plates 311 on piston 7 is provided with lug boss 3111, and lug boss 3111 coordinates that with reentrant part 71 the first slide plate 311 is connected to piston 7 pivotly.For example, in the example of Fig. 2 a, the internal face of reentrant part 71 forms cambered surface, reentrant part 71 inwardly concaves from the outer circumferential face of piston 7, lug boss 3111 protrudes towards the direction of reentrant part 71 from the inner (example lower end as shown in Figure 2 a) of the first slide plate 311, alternatively, the outer wall of lug boss 3111 forms the shape with the shape adaptation of the internal face of reentrant part 71, cooperation by lug boss 3111 and reentrant part 71, the first slide plate 311 can be connected on piston 7, and the first slide plate 311 is swingable with respect to piston 7.Thus, by lug boss 3111 and reentrant part 71 are set, effectively reduced on the one hand the speed of related movement of piston 7 and the first slide plate 311, reduced the sliding friction loss of piston 7 and the first slide plate 311, increase on the other hand the area of contact between piston 7 and the first slide plate 311, reduced end leakage.
Certainly, the invention is not restricted to this, in other embodiments of the present invention, piston 7 is provided with lug boss 3111, the inner of the first slide plate 311 is formed with reentrant part 71, and reentrant part 71 coordinates the first slide plate 311 is connected to pivotly to piston 7(figure not shown with lug boss 3111).
Further, rotary compressor 100 further comprises: two swing lining 312, be formed with respectively curve bath on the opposing sidewalls of the first vane slot 31, two swing linings 312 are contained in two curve baths rotationally, and the first slide plate 311 is located at movably two and swings between linings 312.With reference to Fig. 2-Fig. 6, two curve baths are roughly arc-shaped slot, and two curve bath positioned opposite, the curve bath in left side is recessed left from the left side wall of the first vane slot 31, the curve bath on right side is recessed to the right from the right side wall of the first vane slot 31, two swing lining 312 and are contained in respectively in two curve baths, particularly, each surface contacted with curve bath that swings lining 312 forms the shape with the shape adaptation of the internal face of curve bath, and each surface contacted with the first slide plate 311 that swings lining 312 forms the shape with the shape adaptation of the side wall surface of the first slide plate 311, now each swings lining 312 and is configured to have cambered surface and plane, swinging lining 312 can partly be contained in curve bath, the first slide plate 311 is folded in movably two and swings between lining 312, now the oscillation center O2 of the first slide plate 311 is for swinging the center of rotation of lining 312.Thus, by being set, swing lining 312, the first slide plates 311 can along with the motion of piston 7, swing better.It will be appreciated that, size and the concrete setting position of curve bath in the first vane slot 31 of curve bath and swing lining 312 can be according to the actual requirement settings, to meet better actual requirement.
In another embodiment of the present invention, the first slide plate 311 is one-body molded with piston 7.For example, in the example of Fig. 2 b, the first slide plate 311 is fixedly connected with and is integral with piston 7, particularly, the first slide plate 311 and the whole manufacturing of piston 7, the part that now the first slide plate 311 is piston 7, processing is simple and cost is low.
The first slide plate 311 swings linings 312 pivotly in the first vane slot 31 by two, and the first slide plate 311 swings between lining 312 removable at two.For example, in the example of Fig. 2 b, be formed with respectively curve bath on the opposing sidewalls of the first vane slot 31, two swing lining 312 and are contained in rotationally in two curve baths, the first slide plate 311 is located at movably two and swings between lining 312, swing lining 312 by arranging two, when bent axle 6 drives pistons 7 and moves along the inwall of chamber, piston 7 can drive the first slide plate 311 along the first vane slot 31 move axially and around two axis oscillatings that swing linings 312.
In one embodiment of the invention, the inner of the second slide plate 321 coordinates by pressure switching mechanism 8 separably with the outer circumferential face of piston 7, and pressure switching mechanism 8 is switched the pressure in the second vane slot 32 between low-pressure lateral pressure and high side pressure.As shown in Fig. 3-Fig. 6, when the pressure in the second vane slot 32 is low-pressure lateral pressure, the second slide plate 321 is generally housed in the second vane slot 32, now rotary compressor 100 is high ability mode M, when the pressure in the second vane slot 32 is high side pressure, the inner of the second slide plate 321 extend in chamber and only supports piston 7, and now rotary compressor 100 is low ability mode N.
Alternatively, pressure switching mechanism 8 is three-way valve, and three-way valve has the first valve port 81, the second valve port 82 and the 3rd valve port 83, the first valve ports 81 and communicates with the second vane slot 32, the second valve port 82 communicates with housing 1 inside, and the 3rd valve port 83 communicates with the liquid-storage container 9 of rotary compressor 100.For example, in the example of Fig. 1, the first valve port 81 of three-way valve is communicated with the second vane slot 32, and the second valve port 82 is communicated with holding space, the pipeline connection of the steam outlet pipe 92 of the 3rd valve port 83 and liquid-storage container 9.
Particularly, with reference to Fig. 3, the second vane slot 32 is controlled the pipeline connection with the steam outlet pipe 92 of liquid-storage container 9 by three-way valve, pressure in the second vane slot 32 is low-pressure lateral pressure Ps, under the effect of difference force, the second slide plate 321 is accommodated in the second vane slot 32, with the outer circumferential face of piston 7, does not contact, only have the first slide plate 311 work, now rotary compressor 100 is high ability mode M.
Below in conjunction with Fig. 4 a-Fig. 4 d, to rotary compressor 100, the working principle under high ability mode M and the mobile of refrigerant describe.
With reference to Fig. 4 a-Fig. 4 d, the first slide plate 311 and the one-body molded formation oscillating-piston 7 of piston 7.Because the pressure in the second vane slot 32 is low-pressure lateral pressure Ps, under the effect of difference force, the second slide plate 321 is accommodated in the second vane slot 32.Now, the point of contact between the inwall of the first slide plate 311, piston 7 and chamber is divided into two-part by chamber: the first active chamber and the second active chamber.The low-pressure gas that enters the first active chamber from intakeport 33 is compacted into pressurized gas the second active chamber, while reaching certain pressure, pressurized gas are discharged from first row gas port 41, pressurized gas upwards flow, by driver, for example discharge from the outlet pipe 11 at housing 1 top in stator 21 and the gap between rotor 22 of motor, then from outdoor heat exchanger 201, via throttling arrangement 202, become low-pressure gas in indoor heat exchanger 203, via liquid-storage container 9, from the steam outlet pipe 92 of liquid-storage container 9, by intakeport 33, be inhaled in cylinder 3 again.Under this pattern, due to the discharge capacity that takes full advantage of cylinder 3, so be called high ability mode M.
With reference to Fig. 5, the second vane slot 32 is controlled the internal communication with housing 1 by three-way valve, and the pressure in the second vane slot 32 are high side pressure Pd, under the effect of difference force, the inner of the second slide plate 321 contacts with the outer circumferential face of piston 7, and the first slide plate 311 and the second slide plate 321 are worked simultaneously.Now rotary compressor 100 is low ability mode N.
Below in conjunction with Fig. 6 a-Fig. 6 d, to rotary compressor 100, working principle and the mobile of refrigerant under low ability mode N describes.
With reference to Fig. 6 a-Fig. 6 d, the point of contact between the inwall of the first slide plate 311, the second slide plate 321, piston 7 and chamber is divided into three active chambers by the inner chamber of cylinder 3: the first active chamber, the second active chamber and the 3rd active chamber.The low-pressure gas that enters the first active chamber from intakeport 33 is compacted into pressurized gas the second active chamber, while reaching certain pressure, pressurized gas are discharged from second row gas port 42, pressurized gas upwards flow, by driver, for example discharge from the outlet pipe 11 at housing 1 top in stator 21 and the gap between rotor 22 of motor, then from outdoor heat exchanger 201, via throttling arrangement 202, become low-pressure gas in indoor heat exchanger 203, via liquid-storage container 9, from the steam outlet pipe 92 of liquid-storage container 9, by intakeport 33, be inhaled in cylinder 3 again.In this process, can not suck low-pressure gas by the first slide plate 311 and the 3rd sealed active chamber of the second slide plate 321, thereby the gas be trapped in the 3rd active chamber repeatedly expands and compression under the revolution of piston 7, its pressure is usually low than high side pressure, 41 sealings of first row gas port, so the air-breathing and compression of the 3rd active chamber and rotary compressor 100 is irrelevant.Under this pattern, reduced the actual displacement of cylinder 3, thereby reduced motor load and reduce power consumption, so be called low ability mode N.
In one embodiment of the invention, the angle between the center line of the center line of the first vane slot 31 and the second vane slot 32 is 30 °～330 °.Alternatively, the angle between the center line of the center line of the first vane slot 31 and the second vane slot 32 is 180 °, and now the first vane slot 31 and the second vane slot 32 are along the radially positioned opposite of cylinder 3.It will be appreciated that, the size of the angle between center line that in theory can be by changing the first vane slot 31 and the center line of the second vane slot 32, change the actual displacement of low ability mode N, for example the discharge capacity under high ability mode M is 100%, by changing the size of above-mentioned angle, the discharge capacity under low ability mode N can be designed to 50%, 70%, 90% etc.
Alternatively, driver is variable-frequency motor.The motor speed of rotary compressor 100 and the relation between the relation between cold and motor speed and electric efficiency have been shown in Fig. 7, as can be seen from Figure 7, relation between motor speed and electric efficiency forms an electric efficiency curve L, the electric efficiency of rotary compressor 100 is at 60rps(revolutions per second) left and right the highest, after surpassing 90rps, electric efficiency sharply descends, and when rotating speed is less than 40rps, electric efficiency starts to descend, and from 30rps, to the 20rps electric efficiency, sharply descends.When the electric efficiency of rotary compressor 100, lower than 30rps, the vibration of rotary compressor 100 increases, and the efficiency degradation, thus rotary compressor usually to adopt in use 30rps be lower limit.
According to the rotary compressor 100 of the embodiment of the present invention, under some rotating speeds, rotary compressor 100 can be chosen under high ability mode M or low ability mode N and move, thereby can obtain two kinds of colds, as shown in Figure 7.The discharge capacity of supposing low ability mode N is 50% of high ability mode M, when the rotating speed of motor is 120rps so, the cold of rotary compressor 100 under high ability mode M is 10KW(kilowatt), cold under low ability mode N is 5KW, when being greater than 5KW, cold can only select high ability mode M, in the time of in the scope of cold at 2.5KW～5KW, according to the cold characteristic, can select any one pattern in high ability mode M and low ability mode N to get final product.Select high ability mode M when 2.5KW, the rotating speed of rotary compressor 100 is 30rps, but electric efficiency is lower, selects low ability mode N, and the rotating speed of rotary compressor 100 is 60rps, and now electric efficiency is the highest, more power saving.Especially at 30rps, the refrigerating capacity of rotary compressor 100 under high ability mode M is minimum is 2.5KW, and the refrigerating capacity under low ability mode N minimum be 1.25KW, thereby widened the range of choice in little cold field, can obtain less cold amplitude, and can effectively improve the efficiency of rotary compressor 100, improve travelling comfort.
According to second aspect present invention embodiment's air conditioner 200, comprise rotary compressor 100 according to the above embodiment of the present invention.
In the example of Fig. 8, air conditioner 200 also comprises outdoor heat exchanger 201, indoor heat exchanger 203, throttling arrangement 202 and four-way valve 204, throttling arrangement 202 is located between outdoor heat exchanger 201 and indoor heat exchanger 203, four-way valve 204 has four valve ports, the outlet pipe 11 of rotary compressor 100 and the suction tude 91 of liquid-storage container 9 are connected with two valve ports wherein respectively, and two other valve port is connected with indoor heat exchanger 203 with outdoor heat exchanger 201 respectively.
In one embodiment of the invention, the inner of the second slide plate 321 coordinates by four-way valve 204 separably with the outer circumferential face of piston 7, particularly, the housing 1 of rotary compressor 100 is provided with the pressure switching pipe 12 communicated with the second vane slot 32, and an end of pressure switching pipe 12 is located between four-way valve 204 and outdoor heat exchanger 201.For example, in the example of Fig. 8, pressure switching pipe 12 is located on housing 1, particularly, an end (example is left end as shown in Figure 8) of pressure switching pipe 12 is communicated with the second vane slot 32 in housing 1, the pipeline connection that its other end is connected with outdoor heat exchanger 201 with four-way valve 204.
For example, in air conditioner 200 cooling operations, rotary compressor 100 startings, the pressurized gas of discharging from outlet pipe 11 via four-way valve 204 inflow outdoor heat exchanger 201, through throttling arrangement 202, enter indoor heat exchanger 203, such the first bonding point A is high side pressure Pd, and the pressure in the second vane slot 32 becomes high pressure P d, and now rotary compressor 100 turns round under low ability mode N.But, reversion four-way valve 204, from cooling operation is switched to and heats running, the pressurized gas of discharging from outlet pipe 11 via four-way valve 204 inflow indoor heat exchanger 203, through throttling arrangement 202, enter outdoor heat exchanger 201, such the first bonding point A becomes low-pressure lateral pressure Ps, now rotary compressor 100 turns round under high ability mode M, thereby in air conditioner 200 cooling operation processes, air conditioner 200 can carry out the running that ability is low, and in heating running, air conditioner 200 can carry out the running that ability is high.
According to third aspect present invention embodiment's air conditioner 200, comprise rotary compressor 100 according to the above embodiment of the present invention.
Be all known to those skilled in the art according to other formations and the operation of the air conditioner 200 of the embodiment of the present invention, be not described in detail here.
In the description of this specification, the description of reference term " embodiment ", " some embodiments ", " illustrative examples ", " 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 characteristics of this embodiment or example description.In this manual, the schematic statement of above-mentioned term not necessarily referred to identical embodiment or example.And the specific features of description, structure, material or characteristics can be with suitable mode combinations in any one or more embodiments or example.
Although illustrated and described embodiments of the invention, those having ordinary skill in the art will appreciate that: in the situation that do not break away from principle of the present invention and aim can be carried out multiple variation, modification, replacement and modification to these embodiments, scope of the present invention is limited by claim and equivalent thereof.
Claims (13)
1. a rotary compressor, is characterized in that, comprising:
Housing;
Driver, described driver is located in described housing;
Cylinder, described cylinder is located in described housing and on described cylinder and is formed with the first vane slot and the second vane slot;
Main bearing and supplementary bearing, described main bearing and supplementary bearing are located at respectively top and the bottom of described cylinder and jointly limit chamber with described cylinder;
Bent axle, described bent axle is rotated and is run through described main bearing and described supplementary bearing by described driver drives, is arranged with prejudicially piston on described bent axle, and described piston is rotatable with respect to described bent axle; With
The first slide plate and the second slide plate, described the first slide plate and described the second slide plate are located at respectively in described the first vane slot and described the second vane slot movably, and the inner of described the first slide plate extend in described chamber and is connected with described piston, so that described the first slide plate swings in predetermined angle, and-1.1 * atan(e/R)≤α≤1.1 * atan(e/R), the inner of described the second slide plate coordinates separably with the outer circumferential face of described piston, the offset that wherein e is described bent axle, the radius that R is described cylinder.
2. rotary compressor according to claim 1, it is characterized in that, be formed with reentrant part on described piston, the inner of described the first slide plate is provided with lug boss, and described lug boss coordinates that with the female section described the first slide plate is connected to described piston pivotly.
3. rotary compressor according to claim 2, is characterized in that, further comprises:
Two swing lining, are formed with respectively curve bath on the opposing sidewalls of described the first vane slot, and described two swing linings are contained in two described curve baths rotationally, and described the first slide plate is located at movably described two and swings between linings.
4. rotary compressor according to claim 2, it is characterized in that, described piston is provided with lug boss, and the inner of described the first slide plate is formed with reentrant part, and the female section coordinates that with described lug boss described the first slide plate is connected to described piston pivotly.
5. rotary compressor according to claim 1, is characterized in that, described the first slide plate and described piston are one-body molded,
Described the first slide plate swings linings pivotly in described the first vane slot and swing between linings removable at described two by two.
6. rotary compressor according to claim 1, it is characterized in that, the inner of described the second slide plate coordinates by the pressure switching mechanism separably with the outer circumferential face of described piston, and described pressure switching mechanism is switched the pressure in described the second vane slot between low-pressure lateral pressure and high side pressure.
7. rotary compressor according to claim 6, it is characterized in that, described pressure switching mechanism is three-way valve, described three-way valve has the first to the 3rd valve port, described the first valve port communicates with described the second vane slot, described the second valve port communicates with described enclosure interior, and described the 3rd valve port communicates with the liquid-storage container of described rotary compressor.
8. rotary compressor according to claim 1, is characterized in that, the angle between the center line of the center line of described the first vane slot and described the second vane slot is 30 °～330 °.
9. rotary compressor according to claim 8, is characterized in that, the angle between the center line of the center line of described the first vane slot and described the second vane slot is 180 °.
10. rotary compressor according to claim 1, is characterized in that, described driver is variable-frequency motor.
11. an air conditioner, is characterized in that, comprises rotary compressor as described as any one in claim 1-5,8-10.
12. air conditioner according to claim 11, it is characterized in that, the described housing of described rotary compressor is provided with the pressure switching pipe communicated with described the second vane slot, and an end of described pressure switching pipe is located between the outdoor heat exchanger of the four-way valve of described air conditioner and described air conditioner.
13. an air conditioner, is characterized in that, comprises rotary compressor as described as claim 6 or 7.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013103658009A CN103437999A (en) | 2013-08-20 | 2013-08-20 | Rotary compressor and air conditioner with same |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013103658009A CN103437999A (en) | 2013-08-20 | 2013-08-20 | Rotary compressor and air conditioner with same |
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| CN103437999A true CN103437999A (en) | 2013-12-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2013103658009A Pending CN103437999A (en) | 2013-08-20 | 2013-08-20 | Rotary compressor and air conditioner with same |
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| CN105841387A (en) * | 2016-05-30 | 2016-08-10 | 广东美芝制冷设备有限公司 | Refrigeration device and compressor |
| CN111059319A (en) * | 2018-10-17 | 2020-04-24 | 广东美芝精密制造有限公司 | Three-way valve, compressor assembly, refrigeration device and control method thereof |
| CN116892511A (en) * | 2023-08-25 | 2023-10-17 | 广州航海学院 | Rotary compressor, gas compression system and refrigerating system |
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| CN116892511B (en) * | 2023-08-25 | 2024-04-26 | 广州航海学院 | Rotary compressor, gas compression system and refrigerating system |
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