CN103742410B - Rotary compressor and compression set, air conditioner - Google Patents
Rotary compressor and compression set, air conditioner Download PDFInfo
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- CN103742410B CN103742410B CN201310655852.XA CN201310655852A CN103742410B CN 103742410 B CN103742410 B CN 103742410B CN 201310655852 A CN201310655852 A CN 201310655852A CN 103742410 B CN103742410 B CN 103742410B
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Abstract
The invention discloses a kind of compression set of rotary compressor, comprising: cylinder; Upper bearing (metal) and the lower bearing of chamber is jointly limited with described cylinder; The piston of working space is limited with chamber inner wall; First slide plate and the second slide plate, be separated into the first working room and the second working room by working space; The first intakeport be all communicated with working space and the second intakeport; The first row gas port be all communicated with working space and second exhaust port; First intakeport and the second intakeport are configured to meet the following conditions:
wherein V1 and V2 is respectively the maximum volume of the first and second working rooms, S1 and S2 is respectively the opening area of the first and second intakepories.According to compression set of the present invention, improve the torque fluctuations of rotary compressor, effectively reduce the vibration of rotary compressor, reduce noise, and decrease the increase of cost.
Description
Technical field
The present invention relates to art of refrigeration units, especially relate to a kind of compression set of rotary compressor and there is its rotary compressor, and there is the air conditioner of described rotary compressor.
Background technique
Existing single cylinder rotary compressor as shown in Figure 1, has processing advantage simple, of good performance, is widely used in room air conditioner.But substantially determining the Oscillation Amplitude of compressible machine due to the fluctuation size of moment during compressor operating, vibration of compressor is larger, has not only had a strong impact on the reliability of compressor and air conditioner, has also caused serious noise problem.
Owing to adopting single cylinder eccentric compression technology, in use, pressurized gas moment alters a great deal single cylinder rotary compressor, as shown in " the moment A " in Fig. 4.And vibration of compressor increases along with the discharge capacity increase of compressor, air conditioner noises also increases thereupon, and impact uses.
Compared with single cylinder compressor, the double cylinders rotary compressor with discharge capacity has upper and lower two cylinders, bent axle two eccentric parts 180 ° of layouts, and the change of pressurized gas moment is much smaller, as shown in " the moment B " in Fig. 4, therefore must reach good vibration performance.But compared with single cylinder rotary compressor, there is the many shortcomings increased considerably with fabricating cost of quantity of component in double cylinders rotary compressor, and, owing to adding a set of compression assembly, add friction pair, frictional loss is increased.
Summary of the invention
The present invention is intended at least to solve one of technical problem existed in prior art.For this reason, one object of the present invention is to propose a kind of compression set that can reduce the rotary compressor of noise.
Another object of the present invention is to propose a kind of rotary compressor with described compression set.
Another object of the present invention is to propose a kind of air conditioner with described rotary compressor.
The compression set of a kind of rotary compressor of embodiment, comprising: cylinder according to a first aspect of the present invention, described cylinder hollow and top and bottom-open, and described cylinder is formed with the first vane slot and the second vane slot; Upper bearing (metal) and lower bearing, described upper bearing (metal) and lower bearing are located at the top of described cylinder and bottom respectively jointly to limit chamber with described cylinder; Piston, described piston is driven by eccentric crankshaft and is located at prejudicially in described chamber and can rolls along described chamber inner wall, limits working space between described piston and described chamber inner wall; First slide plate and the second slide plate, described first slide plate and described second slide plate are located in described first vane slot and described second vane slot respectively movably, and the first end of described first slide plate and described second slide plate all to extend in described chamber and only supports to described piston, described working space is separated into the first working room and the second working room by described first slide plate and described second slide plate; First intakeport and the second intakeport, described first intakeport is all communicated with described working space with described second intakeport, and contiguous described first vane slot of described first intakeport is arranged, and contiguous described second vane slot of described second intakeport is arranged; First row gas port and second exhaust port, described first row gas port is all communicated with described working space with second exhaust port, and contiguous described second vane slot of described first row gas port is arranged, and contiguous described first vane slot of described second exhaust port is arranged; Described first intakeport and the second intakeport are configured to meet the following conditions:
wherein V1 is the maximum volume of described first working room, and V2 is the maximum volume of described second working room, and S1 is the opening area of the first intakeport, and S2 is the opening area of the second intakeport.
According to compression set of the present invention, by designing the relation of the volume of the first intakeport and the second intakeport and the first working room and the second working room, improving the torque fluctuations of rotary compressor, effectively reducing the vibration of rotary compressor, reduce noise, and decrease the increase of cost.
According to one embodiment of present invention, the angle θ in the sense of rotation of described bent axle between described slide plate and described second slide plate meets 30≤θ≤330 degree.
Alternatively, described angle θ=180 degree.
According to one embodiment of present invention, described first row gas port is positioned at the upstream of described second vane slot in the sense of rotation of described bent axle, and described second exhaust port is positioned at the upstream of described first vane slot in the sense of rotation of described bent axle.
According to one embodiment of present invention, the first Aspirating valves is provided with in described first intakeport.
According to one embodiment of present invention, the second Aspirating valves is provided with in described second intakeport.The discharge capacity effectively achieving compressor thus increases, and improves compressor performance.
Alternatively, described first slide plate and described piston one-body molded.Effectively reduction even eliminates leakage loss between the first slide plate and piston and frictional loss thus.
According to one embodiment of present invention, described first intakeport and the second intakeport are located in one of them in described cylinder, described upper bearing (metal) and described lower bearing respectively.
Alternatively, in one of them respectively in described cylinder, described upper bearing (metal) and described lower bearing of described first row gas port and described second exhaust port.
Be applied in single cylinder compressor according to the compression set of the embodiment of the present invention, parts only increase a slide plate, eliminate being multiplied of cylinder and piston in existing twin-tub rotation-type compressor, its cost and existing single cylinder rotary compressor very nearly the same, but to obtain with twin-tub rotation-type compressor M curve to similar effect, improve the torque fluctuations of compressor.In addition, also increase Aspirating valves at each intakeport according to compression set of the present invention, significantly can improve the actual exhaust air amount of compressor, thus improve compressor performance.
According to one embodiment of present invention, described compression set also comprises: countercylinder, and described countercylinder is located at the bottom of described cylinder coaxially, described countercylinder is formed with the 3rd vane slot; Central diaphragm, described central diaphragm to be located between described cylinder and described countercylinder and described chamber is separated into upper chamber and lower chambers, wherein said piston to be located in described upper chamber and and limit described working space between the inwall of described upper chamber; Sub-piston, described sub-piston is driven by described eccentric crankshaft and is located at described bottom chamber prejudicially and can rolls along described lower chambers inwall, limits operative minor space between the inwall of described sub-piston and described lower chambers; 3rd slide plate, described 3rd slide plate is located in described 3rd vane slot movably and its first end extend into described bottom chamber and only supports to described sub-piston; 3rd intakeport, contiguous described 3rd vane slot of described 3rd intakeport arranges and is communicated with described operative minor space; 3rd relief opening, contiguous described 3rd vane slot of described 3rd intakeport arranges and is communicated with described operative minor space.
According to one embodiment of present invention, at least one in described first intakeport, the second intakeport and the 3rd intakeport is located on described central diaphragm, and at least one in described first row gas port, second exhaust port and described 3rd relief opening is located on described central diaphragm.
According to one embodiment of present invention, described 3rd intakeport is formed in one of them of described countercylinder, lower bearing and described central diaphragm, and described 3rd relief opening is formed in one of them of described countercylinder, lower bearing and described central diaphragm.
Alternatively, described 3rd intakeport is located on described central diaphragm, and described 3rd relief opening is located at described countercylinder.
According to one embodiment of present invention, in described 3rd intakeport, there is the 3rd Aspirating valves.
According to one embodiment of present invention, described 3rd slide plate and described sub-piston one-body molded.
According to one embodiment of present invention, described countercylinder is formed with the 4th vane slot; And described compression set comprises further: the 4th slide plate, described 4th slide plate is located in described 4th vane slot movably and its first end extend into described bottom chamber and only supports to described sub-piston; 4th intakeport, contiguous described 4th vane slot of described 4th intakeport arranges and is communicated with described operative minor space; 4th relief opening, contiguous described 4th vane slot of described 4th intakeport arranges and is communicated with described operative minor space.
According to one embodiment of present invention, at least one in described first intakeport, the second intakeport, the 3rd intakeport and the 4th intakeport is located on described central diaphragm, and at least one in described first row gas port, second exhaust port, described 3rd relief opening and the 4th relief opening is located on described central diaphragm.
Alternatively, described first intakeport, the second intakeport, the 3rd intakeport and the 4th intakeport are all located on described central diaphragm, and described 3rd relief opening and the 4th relief opening are located on described countercylinder.
According to one embodiment of present invention, described 3rd intakeport and the 4th intakeport are located in one of them of described countercylinder, lower bearing and described central diaphragm respectively, and described 3rd relief opening and the 4th relief opening are located in one of them of described countercylinder, lower bearing and described central diaphragm.
Alternatively, the 4th Aspirating valves is provided with in described 4th intakeport.
According to one embodiment of present invention, described eccentric crankshaft comprises the first eccentric part being arranged with described piston and the second eccentric part being arranged with described sub-piston, and in the sense of rotation of described bent axle, the projected direction of described first eccentric part and the projected direction angle β of described second eccentric part meet 90≤β≤270 °.
Alternatively, described angle β=180 °.
Combine the advantage of single cylinder rotary compressor in previous embodiment and existing twin-tub rotation-type compressor according to the compression set of the embodiment of the present invention, substantially improve the torque fluctuations of compressor further.
A kind of rotary compressor of embodiment, comprises the compression set of the rotary compressor according to a first aspect of the present invention described in embodiment according to a second aspect of the present invention.
A kind of air conditioner of embodiment, comprises and implements described rotary compressor according to a second aspect of the present invention according to a third aspect of the present invention.
Additional aspect of the present invention and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by practice of the present invention.
Accompanying drawing explanation
Above-mentioned and/or additional aspect of the present invention and advantage will become obvious and easy understand from accompanying drawing below combining to the description of embodiment, wherein:
Fig. 1 a and Fig. 1 b is pump body structure and the compression process schematic diagram of prior art single cylinder rotary compressor;
Fig. 2 a and Fig. 2 b is the pump body structure of rotary compressor and compression process schematic diagram that propose according to the present invention;
Fig. 3 a-3d is the working procedure schematic diagram of the rotary compressor that the present invention proposes; Wherein, Fig. 3 a is the schematic diagram of piston when being rotated in initial position; Fig. 3 b is the schematic diagram of piston when being rotated in 90 ° of positions; Fig. 3 c is the schematic diagram of piston when being rotated in 180 ° of positions; Fig. 3 d is the schematic diagram of piston when being rotated in 270 ° of positions;
Fig. 4 is the moment comparison diagram of rotary compressor of the present invention and prior art single cylinder and twin-tub rotation-type compressor;
Fig. 5 is that the pressure loss compares schematic diagram according to an embodiment of the invention;
Fig. 6 is the structural representation of rotary compressor according to an embodiment of the invention;
Fig. 7 is the structural representation of twin-tub rotation-type compressor according to an embodiment of the invention;
Fig. 8 is the second press part structural representation of the rotary compressor shown in Fig. 7;
Fig. 9 is the central diaphragm structural representation of the rotary compressor shown in Fig. 7;
Figure 10 is the structural representation of twin-tub rotation-type compressor according to an embodiment of the invention;
Figure 11 is the second press part structural representation of the rotary compressor shown in Figure 10;
Figure 12 is the central diaphragm structural representation of the rotary compressor shown in Figure 10;
Figure 13 is the schematic diagram of air conditioner in accordance with another embodiment of the present invention.
Reference character:
100: rotary compressor;
1: housing; 11: outlet pipe; 21: stator; 22: rotor;
31: cylinder; 311 first vane slots; 312: the second vane slots;
32: countercylinder; 321 the 3rd vane slots; 322: the four vane slots;
4: upper bearing (metal); 5: lower bearing;
40: chamber; 401: upper chamber; 402: lower chambers;
6: bent axle; 61: the first eccentric parts; 62: the second eccentric parts;
71: first piston; 72: sub-piston 72;
81: the first slide plates; 82: the second slide plates; 83: the three slide plates; 84: the four slide plates
91: first row gas port; 92: second exhaust port; 93: the three relief openings; 94: the four relief openings;
101: the first intakepories; 102: the second intakepories; 103: the three intakepories; 104: the four intakepories;
12: central diaphragm;
131: the first Aspirating valvess; 132: the second Aspirating valvess; 133: the three Aspirating valvess; 134: the four Aspirating valvess;
14: liquid-storage container;
200: air conditioner;
201: outdoor heat exchanger; 202: throttling arrangement;
203: indoor heat exchanger; 204: four-way valve
M1: the first working room; M2: the second working room;
N1: air aspiration cavity; N2: compression chamber; N3: intermediate cavity
Embodiment
Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Being exemplary below by the embodiment be described with reference to the drawings, only for explaining the present invention, and can not limitation of the present invention being interpreted as.
In describing the invention, it will be appreciated that, term " " center ", " on ", D score, "front", "rear", " orientation or the position relationship of the instruction such as " top ", " end " " interior ", " outward " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore can not be interpreted as limitation of the present invention.In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristics.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise one or more these features.In describing the invention, except as otherwise noted, the implication of " multiple " is two or more.
In describing the invention, it should be noted that, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or connect integratedly; Can be mechanical connection, also can be electrical connection; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals.For the ordinary skill in the art, concrete condition above-mentioned term concrete meaning in the present invention can be understood.
Describe the compression set according to the rotary compressor of the embodiment of the present invention below with reference to Fig. 2 a and Fig. 2 b, wherein said rotary compressor also comprises housing 1 and driver 2.Limit holding space in housing 1, driver is located at the top of holding space.Alternatively, driver is motor, is made up of stator 21 and rotor 22.
According to the compression set of the rotary compressor of the embodiment of the present invention, comprise: cylinder 31, upper bearing (metal) 4 and lower bearing 5, piston 71, first slide plate 81 and the second slide plate 82, first intakeport 101 and the second intakeport 102 and first row gas port 91 and second exhaust port 92
As shown in Figure 2 a and 2 b, cylinder 31 hollow and top and bottom-open, cylinder 31 is located at the bottom of holding space and is positioned at the below of driver, and cylinder 31 can be formed as the cylindrical shape that top and bottom are all opened wide.Cylinder 31 is formed with the first vane slot 311 and the second vane slot 312.Specifically, the first vane slot 31 and the second vane slot 32 radially extend and the setting that is spaced apart from each other on the sidewall of cylinder 31.Upper bearing (metal) 4 and lower bearing 5 are located at the top of cylinder 31 and bottom respectively jointly to limit chamber 40 with cylinder 31, piston 71 is driven by eccentric crankshaft 6 and is located at prejudicially in chamber 40 and can rolls along chamber 40 inwall, limits working space between piston 71 and chamber 40 inwall.
Wherein bent axle 6 is rotated by driver drives, and is support by upper bearing (metal) 4 and lower bearing 5, and bent axle 6 is arranged with piston 71 prejudicially.With reference to Fig. 2 a and Fig. 2 b, bent axle 6 extends along the vertical direction and passes upper bearing (metal) 4, cylinder 31 and lower bearing 5 successively, bent axle 6 is provided with eccentric part 61, alternatively, eccentric part 61 is one-body molded with bent axle 6, and piston 71 is set in outside eccentric part 61, when rotary compressor 100 works, eccentric part 61 on driver such as motor driven crankshafts 6 makes eccentric rotary, thus drives piston 71 to move along the inwall of cylinder 31.
First slide plate 81 and the second slide plate 82 are located in the first vane slot 311 and the second vane slot 312 respectively movably, and that is, the first slide plate 81 is located in the first vane slot 311 movably, and the second slide plate 82 is located in the second vane slot 312 movably.In some preferred examples, the angle θ in the sense of rotation of bent axle 6 between slide plate and the second slide plate 82 meets 30≤θ≤330 degree.Preferably, angle θ=180 degree.
The first end of the first slide plate 81 and the second slide plate 82 all extend in chamber 40 and also only supports to piston 71, and working space is separated into the first working room M1 and the second working room M2 by the first slide plate 81 and the second slide plate 82.Specifically, as shown in Fig. 2 a, Fig. 2 b and Fig. 3, the working space between cylinder 31 and piston 71 is separated into left and right Liang Ge work chamber 40, is respectively the first working room M1 and the second working room M2.Piston 71 is divided into two-part the working room at place, air aspiration cavity N1 and compression chamber N2 with the point of contact of cylinder 31, and another complete working room is called intermediate cavity N3.
First intakeport 101 is all communicated with working space with the second intakeport 102, contiguous first vane slot 311 of first intakeport 101 is arranged, contiguous second vane slot 312 of second intakeport 102 is arranged, first row gas port 91 is all communicated with working space with second exhaust port 92, contiguous second vane slot 312 of first row gas port 91 is arranged, and contiguous first vane slot 311 of second exhaust port 92 is arranged.Wherein, the working fluid that should be compressed by the first working room M1 can guide in the first working room M1 by the first intakeport 101, and the working fluid that should be compressed by the second working room M2 can be guided to the second working room M2 by the second intakeport 102.And the working fluid after the first working room M1 compression can guide to outside the first working room M1 by first row gas port 91, the working fluid after the second working room M2 compression guides to outside the second working room M2 by second exhaust port 92
Wherein, the first intakeport 101 and the second intakeport 102 are configured to meet the following conditions:
V1 is the maximum volume of the first working room M1, and V2 is the maximum volume of the second working room M2, and S1 is the opening area of the first intakeport 101, and S2 is the opening area of the second intakeport 102.
Working principle when being used in rotary compressor according to the compression set of the embodiment of the present invention below with reference to Fig. 3 a-Fig. 3 b description and the type of flow of refrigerant, be described for θ=180 °.
With reference to Fig. 3 a-Fig. 3 d, the working space between cylinder 31 and piston 71 is divided into the first working room M1 and the second working room M2 by the first slide plate 81 and the second slide plate 82.The working room at place is divided into two chambeies by the point of contact between the inwall of piston 71 and cylinder 31, is respectively air aspiration cavity N1 and compression chamber N2.Working room complete is in addition called intermediate cavity N3.
At 0 ° within the scope of 90 °, the volume being in the compression chamber N2 in the first working room M1 constantly reduces, and pressure constantly raises, and is in volume and the second working room M2(and intermediate cavity N3 of the air aspiration cavity N1 in the first working room M1) volume constantly increase.
At 90 ° within the scope of 180 °, the volume being in the compression chamber N2 in the first working room M1 reduces further, and compression chamber N2 pressure continues to raise, and when reaching certain pressure, working fluid discharges the first working room M1 from first row gas port 91.Be in the air aspiration cavity N1 in the first working room M1 volume continue increase, and the second working room M2(and intermediate cavity N3) volume constantly reduce.
At 180 ° within the scope of 270 °, air aspiration cavity N1 and compression chamber N2 is in the second working room M2, and intermediate cavity N3 is the first working room M1.The volume of compression chamber N2 constantly reduces, and pressure constantly raises, and air aspiration cavity N1 and intermediate cavity N3(i.e. the first working room M1) volume constantly increase.
At 270 ° within the scope of 360 °, the volume being in the compression chamber N2 in the second working room M2 reduces further, and compression chamber N2 pressure continues to raise, and when reaching certain pressure, working fluid discharges the second working room M2 from second exhaust port 92.Be in the air aspiration cavity N1 in the second working room M2 volume continue increase, and the first working room M1(and intermediate cavity N3) volume constantly reduce.
The working fluid of discharging from first row gas port 91 and second exhaust port 92 upwards flows, discharged from the outlet pipe 11 at housing 1 top by the gap between the stator 21 of driver such as motor and rotor 22, then outdoor heat exchanger 201, via throttling arrangement 202, low-pressure gas is become in indoor heat exchanger 203, again via liquid-storage container 14, be inhaled into the first working room M1 and the second working room M2 respectively by the first intakeport 101, second intakeport 102.
Bent axle 6 revolves and turns around, air aspiration cavity N1 and compression chamber N2 alternately occurs at Liang Ge working room (the first working room M1 and the second working room M2), three active chambers work simultaneously, its volume mechanical periodicity, thus complete the whole work cycle of compressor, bent axle 6 often revolves and turns around, exhaust twice, as illustrated in figs. 3 a-3d.
Due to this working principle, torque ripple is confidential less than existing single cylinder rotary compression in the course of the work to make rotary compressor of the present invention, thus vibration of compressor is reduced greatly, close to the level of existing twin-tub rotation-type compressor, as shown in Figure 4.
Can find from Fig. 3 a-Fig. 3 b, at 0 ° within the scope of 180 °, intermediate cavity N3 is the second working room M2, communicates with the second intakeport 102, its volume first increases and then decreases.90 ° time, reach maximum value.If do not have Aspirating valves in the second intakeport 102, after bent axle 6 turns over 90 °, the workflow cognition of intermediate cavity N3 is flowed backward to outside the second working room M2 by the second intakeport 102.Therefore when the maximum volume V2 of the second working room M2 occurs in 90 °.
Can find from Fig. 3 c-Fig. 3 d, at 180 ° within the scope of 360 °, intermediate cavity N3 is the first working room M1, communicates with the first intakeport 101, its volume first increases and then decreases.270 ° time, reach maximum value.If do not have Aspirating valves in the first intakeport 101, after bent axle 6 turns over 270 °, the workflow cognition of intermediate cavity N3 is flowed backward to outside the first working room M1 by the first intakeport 101.Therefore when the maximum volume V1 of the first working room M1 occurs in 270 °.
The impact that air-breathing circulation area is lost pressure of inspiration(Pi) is larger, can carry out simplify processes herein with pressure loss in piping,
Wherein, (P
2-P
1) be the pressure loss;
ρ is the density of working fluid;
λ is the friction factor between working fluid and pipeline;
L is length of pipe;
D
hfor the hydraulic diameter of pipeline;
U is the flow velocity of working fluid;
In general, circulates area is larger, means that the hydraulic diameter of pipeline is larger; Under same flow, the flow velocity flowing through pipeline is less, and pressure loss in piping is less, as shown in Figure 5.
If the flow velocity difference of operating fluid crosses first intakeport 101 and the second intakeport 102 is larger, both pressure of inspiration(Pi) loss difference is obvious, make the skewness of working fluid, the fluid mass finally entering the first working room M1 and the second working room M2 is caused to change, cause poor inspiration, effective gettering quantity declines.
In order to avoid the generation of the problems referred to above, must the opening area S1 of appropriate design first the intakeport 101 and opening area S2 of the second intakeport 102.Thus, the present invention proposes the first intakeport 101 and the second intakeport 102 is configured to meet the following conditions:
Can effectively solve the problem thus.
To sum up, according to compression set of the present invention, by designing the relation of the volume of the first intakeport 101 and the second intakeport 102 and the first working room and the second working room, improve the torque fluctuations of rotary compressor, the vibration of effective reduction rotary compressor, reduce noise, and decrease the increase of cost.
According to an example of the present invention, as shown in Figure 2 b, first row gas port 91 is positioned at the upstream of the second vane slot 312 in the sense of rotation of bent axle 6, and second exhaust port 92 is positioned at the upstream of the first vane slot 311 in the sense of rotation of bent axle 6.Wherein, it should be noted that, " upstream " can be understood as the upstream of the flow direction of refrigerant in chamber 40.
In addition, during in order to ensure that intermediate cavity N3 volume reaches maximum, the working fluid sucked from suction port does not flow backwards intermediate cavity N3, is necessary to arrange Aspirating valves in intakeport.According to a preferred exemplary of the present invention, in the first intakeport 101, be provided with the first Aspirating valves 131.Further, the second Aspirating valves 132 is provided with in the second intakeport 102.As shown in Fig. 2 a and Fig. 2 b, the discharge capacity effectively achieving compressor thus increases, and improves compressor performance.
In an example of the present invention, the first slide plate 81 and piston 7 integrated design, effective reduction even eliminates leakage loss between the first slide plate 81 and piston 7 and frictional loss.As in the example of fig. 6, the first slide plate 81 is fixedly connected with integral with piston 7, one-body molded, and particularly, the first slide plate 81 and the manufacture of piston 7 overall processing, now the first slide plate 81 is a part for piston 7, and processing is simple and cost is low.Certainly, the present invention is not limited thereto, the first slide plate 81 and piston 7 can also realize integrated design by the mode such as hinged.
According to some embodiments of the present invention, the first intakeport 101 and the second intakeport 102 are located in one of them in cylinder 31, upper bearing (metal) 4 and lower bearing 5 respectively.Alternatively, the first intakeport 101, second intakeport 102, first row gas port 91 and second exhaust port 92 are all formed on cylinder 31.Similarly, according to some embodiments of the present invention, in one of them respectively in cylinder 31, upper bearing (metal) 4 and lower bearing 5 of first row gas port 91 and second exhaust port 92.
Thus, compression set according to the embodiment of the present invention has done improvement in traditional single cylinder rotary type compressor pump body provided therewith, namely at increase slide plate, simultaneously correspondingly add an intakeport and a relief opening, two slide plates are separated into two independently working rooms the space between cylinder and piston, bent axle is often gone around just can realize twice exhaust, therefore makes the torque fluctuations of compressor improve, as shown in " moment C " in Fig. 4.
To sum up, be applied in single cylinder compressor according to the compression set of the embodiment of the present invention, parts only increase a slide plate, eliminate being multiplied of cylinder and piston in existing twin-tub rotation-type compressor, its cost and existing single cylinder rotary compressor very nearly the same, but to obtain with twin-tub rotation-type compressor M curve to similar effect, improve the torque fluctuations of compressor.In addition, also increase Aspirating valves at each intakeport according to compression set of the present invention, significantly can improve the actual exhaust air amount of compressor, thus improve compressor performance.
Each embodiment above-described is the compression set of the rotary compressor with single cylinder.But the compression set according to the embodiment of the present invention can also realize in the mode of twin-tub.With reference to figure 7 and Fig. 8, on the basis of above-mentioned compression set, add the structure of parts such as countercylinder 32 grade.To be described in detail below.
According to another embodiment of the invention, compression set also comprises: countercylinder 32, central diaphragm 12, sub-piston 72, the 3rd slide plate 83, the 3rd intakeport 103 and the 3rd relief opening 93.Now bent axle 6 comprises the first eccentric part being arranged with piston 71 and the second eccentric part being arranged with sub-piston 72, and in the sense of rotation of bent axle 6, the projected direction of the first eccentric part and the projected direction angle β of the second eccentric part meet 90≤β≤270 °.Preferably, angle β=180 °.
As in figures 7-9, countercylinder 32 is located at the bottom of cylinder 31 coaxially, countercylinder 32 is formed with the 3rd vane slot 321, central diaphragm 12 to be located between cylinder 31 and countercylinder 32 and chamber 40 is separated into upper chamber 401 and lower chambers 402, and wherein piston 71 to be located in upper chamber 401 and and to limit working space between the inwall of upper chamber 401.Sub-piston 72 is driven by eccentric crankshaft 6 and is located at prejudicially in lower chambers 402 and can rolls along lower chambers 402 inwall, limits operative minor space between the inwall of sub-piston 72 and lower chambers 402.
3rd slide plate 83 is located in the 3rd vane slot 321 movably and its first end to extend in lower chambers 402 and only supports to sub-piston 72, contiguous 3rd vane slot 321 of 3rd intakeport 103 arranges and is communicated with operative minor space, and contiguous 3rd vane slot 321 of the 3rd intakeport 103 arranges and is communicated with operative minor space.The working principle of each active chamber of countercylinder 32 and the similar of cylinder 31, no longer carefully state at this.
According to some optional examples, at least one in the first intakeport 101, second intakeport 102 and the 3rd intakeport 103 is located on central diaphragm 12, and at least one in first row gas port 91, second exhaust port 92 and the 3rd relief opening 93 is located on central diaphragm 12.
According to other optional examples, 3rd intakeport 103 is formed in one of them of countercylinder 32, lower bearing 5 and central diaphragm 12,3rd relief opening 93 is formed in one of them of countercylinder 32, lower bearing 5 and central diaphragm 12, such as the 3rd intakeport 103 is located on central diaphragm 12, and the 3rd relief opening 93 is located at countercylinder 32, as shown in figs. 7 to 9.
Similarly, in order to prevent the working fluid sucked from the 3rd intakeport from not flow backwards intermediate cavity N3, there is in the 3rd intakeport 103 the 3rd Aspirating valves 133.In addition, as above-mentioned first slide plate 81 and piston 71 similarly, the 3rd slide plate 83 and sub-piston 72 also can be one-body molded.
According to still a further embodiment, the basis of above-described embodiment can also increase again the dependency structure of the 4th slide plate.Specifically, as shown in Figure 10-Figure 11, countercylinder 32 can also be formed the 4th vane slot 322, and compression set comprises further: the 4th slide plate 84, the 4th intakeport 104 and the 4th relief opening 94,4th slide plate 84 is located in the 4th vane slot 322 movably and its first end to extend in lower chambers 402 and only supports to sub-piston 72, contiguous 4th vane slot 322 of 4th intakeport 104 arranges and is communicated with operative minor space, and contiguous 4th vane slot 322 of the 4th intakeport 104 arranges and is communicated with operative minor space.
In some optional examples, at least one in first intakeport 101, second intakeport 102, the 3rd intakeport 103 and the 4th intakeport 104 is located on central diaphragm 12, and at least one in first row gas port 91, second exhaust port 92, the 3rd relief opening 93 and the 4th relief opening 94 is located on central diaphragm 12.Such as, the first intakeport 101, second intakeport 102, the 3rd intakeport 103 and the 4th intakeport 104 are all located on central diaphragm 12, and as shown in figure 12, the 3rd relief opening 93 and the 4th relief opening 94 are located on countercylinder 32.
In other optional examples, 3rd intakeport 103 and the 4th intakeport 104 are located in one of them of countercylinder 32, lower bearing 5 and central diaphragm 12 respectively, and the 3rd relief opening 93 and the 4th relief opening 94 are located in one of them of countercylinder 32, lower bearing 5 and central diaphragm 12.
Similar also with cylinder 31 of the working principle adding each active chamber of the countercylinder 32 of the 4th vane slot 84, is not described in detail at this.Wherein, during in order to ensure that intermediate cavity N3 volume reaches maximum, the working fluid sucked from suction port does not flow backwards intermediate cavity N3, is provided with the 4th Aspirating valves 134, in the 4th intakeport 104 as shown in Figure 10-Figure 11.。
Combine the advantage of single cylinder rotary compressor in previous embodiment and existing twin-tub rotation-type compressor according to the compression set of the embodiment of the present invention, substantially improve the torque fluctuations of compressor further.
A kind of rotary compressor of embodiment, comprises the compression set of the rotary compressor according to previous embodiment of the present invention according to a second aspect of the present invention.According to the rotary compressor of the embodiment of the present invention other form and operation be all known for those of ordinary skills, be not described in detail here.
As shown in figure 13, a kind of air conditioner of embodiment, comprises the rotary compressor according to a second aspect of the present invention described in embodiment according to a third aspect of the present invention.In the example in figure 13, air conditioner 200 is heating and air conditioner, also comprise 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 wherein two valve ports respectively, and two other valve port is connected with indoor heat exchanger 203 with outdoor heat exchanger 201 respectively.
According to the air conditioner 200 of the embodiment of the present invention other form and operation be all known to those skilled in the art, be also not described in detail here.
In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " illustrative examples ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, identical embodiment or example are not necessarily referred to the schematic representation of above-mentioned term.And the specific features of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.
Although illustrate and describe embodiments of the invention, those having ordinary skill in the art will appreciate that: can carry out multiple change, amendment, replacement and modification to these embodiments when not departing from principle of the present invention and aim, scope of the present invention is by claim and equivalents thereof.
Claims (24)
1. a compression set for rotary compressor, is characterized in that, comprising:
Cylinder, described cylinder hollow and top and bottom-open, and described cylinder is formed with the first vane slot and the second vane slot;
Upper bearing (metal) and lower bearing, described upper bearing (metal) and lower bearing are located at the top of described cylinder and bottom respectively jointly to limit chamber with described cylinder;
Piston, described piston is driven by eccentric crankshaft and is located at prejudicially in described chamber and can rolls along described chamber inner wall, limits working space between described piston and described chamber inner wall;
First slide plate and the second slide plate, described first slide plate and described second slide plate are located in described first vane slot and described second vane slot respectively movably, and the first end of described first slide plate and described second slide plate all to extend in described chamber and only supports to described piston, described working space is separated into the first working room and the second working room by described first slide plate and described second slide plate;
First intakeport and the second intakeport, described first intakeport is all communicated with described working space with described second intakeport, and contiguous described first vane slot of described first intakeport is arranged, and contiguous described second vane slot of described second intakeport is arranged;
First row gas port and second exhaust port, described first row gas port is all communicated with described working space with second exhaust port, and contiguous described second vane slot of described first row gas port is arranged, and contiguous described first vane slot of described second exhaust port is arranged;
Described first intakeport and the second intakeport are configured to meet the following conditions:
V1 is the maximum volume of described first working room, and V2 is the maximum volume of described second working room, and S1 is the opening area of the first intakeport, and S2 is the opening area of the second intakeport.
2. compression set according to claim 1, is characterized in that, the angle θ in the sense of rotation of described bent axle between described slide plate and described second slide plate meets 30≤θ≤330 degree.
3. compression set according to claim 2, is characterized in that, described angle θ=180 degree.
4. compression set according to claim 1, it is characterized in that, described first row gas port is positioned at the upstream of described second vane slot in the sense of rotation of described bent axle, and described second exhaust port is positioned at the upstream of described first vane slot in the sense of rotation of described bent axle.
5. compression set according to claim 1, is characterized in that, is provided with the first Aspirating valves in described first intakeport.
6. compression set according to claim 1, is characterized in that, is provided with the second Aspirating valves in described second intakeport.
7. compression set according to claim 1, is characterized in that, described first slide plate and described piston one-body molded.
8. compression set according to claim 1, is characterized in that, described first intakeport and the second intakeport are located in one of them in described cylinder, described upper bearing (metal) and described lower bearing respectively.
9. compression set according to claim 8, is characterized in that, in one of them respectively in described cylinder, described upper bearing (metal) and described lower bearing of described first row gas port and described second exhaust port.
10. the compression set according to any one of claim 1-7, is characterized in that, also comprises:
Countercylinder, described countercylinder is located at the bottom of described cylinder coaxially, described countercylinder is formed with the 3rd vane slot;
Central diaphragm, described central diaphragm to be located between described cylinder and described countercylinder and described chamber is separated into upper chamber and lower chambers, wherein said piston to be located in described upper chamber and and limit described working space between the inwall of described upper chamber;
Sub-piston, described sub-piston is driven by described eccentric crankshaft and is located at described bottom chamber prejudicially and can rolls along described lower chambers inwall, limits operative minor space between the inwall of described sub-piston and described lower chambers;
3rd slide plate, described 3rd slide plate is located in described 3rd vane slot movably and its first end extend into described bottom chamber and only supports to described sub-piston;
3rd intakeport, contiguous described 3rd vane slot of described 3rd intakeport arranges and is communicated with described operative minor space;
3rd relief opening, contiguous described 3rd vane slot of described 3rd intakeport arranges and is communicated with described operative minor space.
11. compression sets according to claim 10, it is characterized in that, at least one in described first intakeport, the second intakeport and the 3rd intakeport is located on described central diaphragm, and at least one in described first row gas port, second exhaust port and described 3rd relief opening is located on described central diaphragm.
12. compression sets according to claim 10, it is characterized in that, described 3rd intakeport is formed in one of them of described countercylinder, lower bearing and described central diaphragm, and described 3rd relief opening is formed in one of them of described countercylinder, lower bearing and described central diaphragm.
13. compression sets according to claim 12, is characterized in that, described 3rd intakeport is located on described central diaphragm, and described 3rd relief opening is located at described countercylinder.
14. compression sets according to claim 10, is characterized in that, have the 3rd Aspirating valves in described 3rd intakeport.
15. compression sets according to claim 10, is characterized in that, described 3rd slide plate and described sub-piston one-body molded.
16. compression sets according to claim 10, is characterized in that, described countercylinder are formed with the 4th vane slot; And described compression set comprises further:
4th slide plate, described 4th slide plate is located in described 4th vane slot movably and its first end extend into described bottom chamber and only supports to described sub-piston;
4th intakeport, contiguous described 4th vane slot of described 4th intakeport arranges and is communicated with described operative minor space;
4th relief opening, contiguous described 4th vane slot of described 4th relief opening arranges and is communicated with described operative minor space.
17. compression sets according to claim 16, it is characterized in that, at least one in described first intakeport, the second intakeport, the 3rd intakeport and the 4th intakeport is located on described central diaphragm, and at least one in described first row gas port, second exhaust port, described 3rd relief opening and the 4th relief opening is located on described central diaphragm.
18. compression sets according to claim 17, is characterized in that, described first intakeport, the second intakeport, the 3rd intakeport and the 4th intakeport are all located on described central diaphragm, and described 3rd relief opening and the 4th relief opening are located on described countercylinder.
19. compression sets according to claim 16, it is characterized in that, described 3rd intakeport and the 4th intakeport are located in one of them of described countercylinder, lower bearing and described central diaphragm respectively, and described 3rd relief opening and the 4th relief opening are located in one of them of described countercylinder, lower bearing and described central diaphragm.
20. compression sets according to claim 16, is characterized in that, are provided with the 4th Aspirating valves in described 4th intakeport.
21. compression sets according to claim 10, it is characterized in that, described eccentric crankshaft comprises the first eccentric part being arranged with described piston and the second eccentric part being arranged with described sub-piston, and in the sense of rotation of described bent axle, the projected direction of described first eccentric part and the projected direction angle β of described second eccentric part meet 90≤β≤270 °.
22. compression sets according to claim 21, is characterized in that, described angle β=180 °.
23. 1 kinds of rotary compressors, is characterized in that, comprise the compression set of the rotary compressor according to any one of claim 1-22.
24. 1 kinds of air conditioners, is characterized in that, comprise rotary compressor according to claim 23.
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| Publication number | Priority date | Publication date | Assignee | Title |
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| EP3078859B1 (en) * | 2013-12-05 | 2023-09-13 | Guangdong Meizhi Compressor Co., Ltd. | Rotary compressor and compression unit thereof, and air conditioner |
| CN105114311A (en) * | 2015-08-24 | 2015-12-02 | 广东美芝制冷设备有限公司 | Multi-cylinder rotary compressor and refrigeration device with same |
| CN105221420A (en) * | 2015-10-22 | 2016-01-06 | 珠海凌达压缩机有限公司 | Refrigerating system and single-cylinder double-sliding-piece compressor thereof |
| EP3492748B1 (en) * | 2016-07-28 | 2020-09-16 | Guangdong Meizhi Compressor Co., Ltd. | Compressor as well as cooling-heating refrigeration device and cooling-only refrigeration device having same |
| CN106704188B (en) * | 2017-02-24 | 2018-09-11 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigeration system with it |
| CN106762640B (en) * | 2017-02-24 | 2018-09-28 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigeration system with it |
| CN107461955A (en) * | 2017-08-30 | 2017-12-12 | 广东美芝制冷设备有限公司 | Refrigeration system |
| CN110080987B (en) * | 2019-05-09 | 2024-07-02 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN110594154A (en) * | 2019-09-06 | 2019-12-20 | 珠海凌达压缩机有限公司 | Compressor, air conditioner refrigerating system and air conditioner |
| CN112746963B (en) * | 2019-10-31 | 2022-06-14 | 广东美的白色家电技术创新中心有限公司 | Compressor, compressor assembly, heat exchange system and electrical equipment |
| CN110863986B (en) * | 2019-11-29 | 2022-07-12 | 安徽美芝精密制造有限公司 | Compressor and refrigeration equipment |
| CN110778498B (en) * | 2019-11-29 | 2022-03-22 | 安徽美芝精密制造有限公司 | Compressor and refrigeration equipment |
| CN110863985A (en) * | 2019-11-29 | 2020-03-06 | 安徽美芝精密制造有限公司 | Compressor and refrigeration equipment |
| CN110985383A (en) * | 2019-11-29 | 2020-04-10 | 安徽美芝精密制造有限公司 | Compressor and refrigeration equipment |
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