CN104806526A - Rotating compressor - Google Patents
Rotating compressor Download PDFInfo
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- CN104806526A CN104806526A CN201510152074.1A CN201510152074A CN104806526A CN 104806526 A CN104806526 A CN 104806526A CN 201510152074 A CN201510152074 A CN 201510152074A CN 104806526 A CN104806526 A CN 104806526A
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- rotor
- rotary compressor
- bent axle
- eccentric part
- equilibrium block
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- 230000005484 gravity Effects 0.000 claims description 28
- 238000013016 damping Methods 0.000 claims description 18
- 238000000034 method Methods 0.000 description 18
- 238000013461 design Methods 0.000 description 15
- 230000007246 mechanism Effects 0.000 description 8
- 230000000694 effects Effects 0.000 description 7
- 230000008859 change Effects 0.000 description 6
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000030279 gene silencing Effects 0.000 description 2
- 230000006698 induction Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000011148 porous material Substances 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 1
- 240000004859 Gamochaeta purpurea Species 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 238000012512 characterization method Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000013632 homeostatic process Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000011176 pooling Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000001308 synthesis method Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a rotating compressor which comprises a motor, a crank shaft, a piston, a torque buffer device and one or more balance blocks, wherein the motor comprises a stator and a rotor; the crank shaft rotationally slides with the rotor, and comprises a main shaft, an eccentric part and an auxiliary shaft in sequence; the piston is driven by the eccentric part; the torque buffer device is connected with the rotor and the crank shaft respectively; the balance blocks are used for offsetting unbalance mass generated due to rotating of the eccentric part and the piston, and positioned in the crank shaft. The rotating vibration of the rotating compressor can be reduced, the rotating angle of the rotor is changed, and the normal line vibration is not increased.
Description
Technical field
The present invention relates to refrigerating field, especially relate to a kind of rotary compressor.
Background technique
Adopt in the rotary compressor of DC variable-frequency motor, in order to reduce rotary vibration, while detection rotor rotary position, have detected crankshaft torque variation, carrying out the Waveform composition of frequency variator.But the problem of this motor torque control technology not only can only adopt in the rotary compressor of DC motor, and electric efficiency can decline.
Summary of the invention
The present invention is intended to solve one of technical problem in correlation technique at least to a certain extent.
For this reason, the present invention proposes a kind of rotary compressor, can reduce the rotary vibration of rotary compressor, and the angle of swing of rotor changes, and method linearly coupled also can not increase.
The rotary compressor of embodiment according to a first aspect of the present invention, comprising: the motor with stators and rotators; The bent axle formed by main shaft, eccentric part and countershaft order of rotational slide is carried out with described rotor; By the piston that described eccentric part drives; Connect the moment damping device of described rotor and described bent axle respectively; At least one equilibrium block of offsetting the unbalance mass, that the rotation due to described eccentric part and described piston produces possesses in described bent axle.
According to the rotary compressor of the embodiment of the present invention, by being provided with moment damping device, the rotary vibration of rotary compressor can be reduced, simultaneously by being provided with the equilibrium block of the unbalance mass, of the rotation generation for offsetting eccentric part and piston on bent axle, even if therefore the angle of swing of rotor changes, method linearly coupled also can not increase.
In some embodiments of the invention, described rotary compressor is twin-tub rotation-type compressor, and the unbalance mass, that the rotation due to eccentric part described in two groups and piston produces offset by described equilibrium block.
In some embodiments of the invention, described equilibrium block is located between described eccentric part and described countershaft or in the axial end portion of described countershaft.
Particularly, described moment damping device is torsion bar spring or torsion-coil spring.
According to some embodiments of the present invention, within the scope of the rotational slide of described bent axle, possesses the groove described main shaft being carried out to path.
According to some embodiments of the present invention, within the scope of the rotational slide of described bent axle, possesses the thin-walled portion of the quality of the side reducing described bent axle.
According to some embodiments of the present invention, the axial end of described main shaft is also provided with the axle head equilibrium block for offsetting described unbalance mass.
According to some embodiments of the present invention, described rotor is also provided with the rotor balance for offsetting described unbalance mass.
According to a further embodiment of the invention, by the reference line in the center of gravity of described unbalance mass, and the axle center of described eccentric part, be θ with the angle of the equilibrium block center of gravity line in the axle center by described rotor balance center of gravity and described rotor, before described rotor startup, θ is the scope from 3 degree to 90 degree, in the sense of rotation of described rotor, the center of gravity line of described rotor balance is positioned at after described reference line.
Accompanying drawing explanation
Fig. 1 is relevant to embodiments of the invention 1, represents the longitudinal section of rotary compressor inside;
The details drawing that Fig. 2 is relevant to this embodiment 1, represent bent axle and homeostasis technology;
Fig. 3 is relevant to this embodiment 1, the sectional view of bent axle;
The detail drawing that Fig. 4 is relevant to this embodiment 1, relevant with the assembling of compressing mechanism;
Fig. 5 is relevant to this embodiment 1, the ssembly drawing of compressing mechanism and rotor;
Fig. 6 is relevant to this embodiment 1, alternate design is routine;
Fig. 7 is relevant to embodiments of the invention 2, the allocation plan of equilibrium block;
The allocation plan that Fig. 8 is relevant to embodiments of the invention 3, represent equilibrium block;
Fig. 9 is relevant to this embodiment 3, the action specification figure of resultant vector;
Figure 10 is relevant to embodiments of the invention 4, the compression key element of twin-tub rotation-type compressor and the ssembly drawing of rotor;
Figure 11 is relevant to embodiments of the invention 5, the component figure of torsion-coil spring;
Figure 12 is relevant to this embodiment 5, spring assembling figure to rotor;
Figure 13 is relevant to this embodiment 5, the planimetric map of rotor assembling.
Reference character:
Rotary compressor 1, housing 2, compressing mechanism 5, piston 21, cylinder 20, supplementary bearing 26, central diaphragm 27,
Motor 3, stator 4, rotor 30, end ring 32a, rotor balance 38,
Bent axle 10, main shaft 11, axle mesopore 11a, eccentric part 13, thin journal axle 12, countershaft 14, countershaft equilibrium block 15, main shaft cutting portion 12a, cross-drilled hole 11d, countershaft end equilibrium block 18, opening slot 11b, pore 13c,
Torsion bar spring 40, C motion end 46, R motion end 45, turn round axle 41, R moment rod 43,
Pipe 35, silencing apparatus 26a, axle head equilibrium block 36, C shelves ring 39,
Torsion-coil spring 60, coil portion 61, R motion end 65, C motion end 66,
Embodiment
Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.
In describing the invention, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", " outward ", " clockwise ", " counterclockwise ", " axis ", " radial direction ", orientation or the position relationship of the instruction such as " circumference " 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 limitation of the present invention can not be interpreted as.
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 at least one this feature.In describing the invention, the implication of " multiple " is at least two, such as two, three etc., unless otherwise expressly limited specifically.
In the present invention, unless otherwise clearly defined and limited, the term such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be mechanical connection, also can be electrical connection or each other can communication; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements, unless otherwise clear and definite restriction.For the ordinary skill in the art, above-mentioned term concrete meaning in the present invention can be understood as the case may be.
Be described the rotary compressor 1 according to the embodiment of the present invention below with reference to Fig. 1-Figure 13, wherein rotary compressor 1 can be single cylinder rotary compressor, also can be twin-tub rotation-type compressor.
The rotary compressor 1 of embodiment according to a first aspect of the present invention, rotary compressor 1 can be single cylinder rotary compressor, rotary compressor 1 comprises: motor 3, bent axle 10, piston 21 and moment damping device, and wherein, motor 3 has stator 4 and rotor 30.Bent axle 10 and rotor 30 carry out rotational slide, and main shaft 11, eccentric part 13 and countershaft 14 order composition pressed by bent axle 10.Piston 21 is driven rotation by eccentric part 13.Moment damping device connects rotor 30 and bent axle 10 respectively, and particularly, moment damping device can be torsion bar spring 40 or torsion-coil spring 60.
At least one equilibrium block of offsetting the unbalance mass, that the rotation due to eccentric part 13 and piston 21 produces possesses in bent axle 10.
When the rotor 30 of motor 3 is with dynamic crankshaft 10 to rotate, eccentric part 13 driven plunger 21 carries out eccentric rotary with pressurized gas, so bent axle 10 produces axle moment sharply, because moment damping device makes bent axle 10 and rotor 30 carry out rotational slide, moment damping device has relaxed the variation of this axle moment, the angular velocity of rotor 30 is stablized, therefore can reduce the rotary vibration of rotary compressor 1.The equilibrium block possessed in bent axle 10 can offset the unbalance mass, that the rotation due to eccentric part 13 and piston 21 produces.
According to the rotary compressor 1 of the embodiment of the present invention, by being provided with moment damping device, the rotary vibration of rotary compressor 1 can be reduced, simultaneously by being provided with the equilibrium block of the unbalance mass, of the rotation generation for offsetting eccentric part 13 and piston 21 on bent axle 10, even if therefore the angle of swing of rotor 30 changes, method linearly coupled also can not increase.
Particularly, equilibrium block can be located between eccentric part 13 and countershaft 14 or in the axial end portion of countershaft 14.As Figure 2-Figure 5, equilibrium block is located between eccentric part 13 and countershaft 14, equilibrium block can be called countershaft equilibrium block 15.As shown in Figure 6, equilibrium block is located in the axial end portion of countershaft 14, equilibrium block can be called countershaft end equilibrium block 18.
As shown in Figure 2, in specific embodiments more of the present invention, within the scope of the rotational slide of bent axle 10, possess groove main shaft 11 being carried out to path, in brief, a part for main shaft 11 attenuates to be formed as thin journal axle 12, thus can improve slippage loss.
As shown in Figure 2, in some embodiments of the invention, within the scope of the rotational slide of bent axle 10, the thin-walled portion of the quality of the side reducing bent axle 10 is possessed.That is, bent axle 10 is provided with the main shaft cutting portion 12a reducing bent axle 10 quality, and more specifically, main shaft cutting portion 12a is located in thin journal axle 12.
According to some embodiments of the present invention, as shown in Figure 7, the axial end of main shaft 11 is also provided with the axle head equilibrium block 36 for offsetting unbalance mass.
In some embodiments of the invention, as shown in Figure 8, rotor 30 is also provided with the quantum balancing block 38 for offsetting unbalance mass, wherein rotor balance 38 is arranged on the end face away from eccentric part 13 of rotor 30.
In order to avoid causing the increase of method linearly coupled owing to arranging rotor balance 38, in further embodiment of the present invention, by the reference line A-C1 in the center of gravity of unbalance mass, and the axle center of eccentric part 13, be θ with the angle of the equilibrium block center of gravity line B1-B1 in the axle center by rotor balance center of gravity and rotor 30, it is scope from 3 degree to 90 degree that rotor 30 starts front θ, in the sense of rotation of rotor 30, the center of gravity line of rotor balance 38 is positioned at after reference line.
The rotary compressor of embodiment according to a second aspect of the present invention, rotary compressor is twin-tub rotation-type compressor, rotary compressor comprises: motor 3, bent axle 10a, piston 21a, 21b and moment damping device, and wherein, motor 3 has stator 4 and rotor 30.Bent axle 10a and rotor 30 carry out rotational slide, and bent axle 10a presses main shaft 11, eccentric part 13a, 13b and countershaft 14 order composition.Piston 21a is driven by eccentric part 13a and rotates, and piston 21b is driven by eccentric part 13b and rotates.Moment damping device connects rotor 30 and bent axle 10a respectively, and particularly, moment damping device can be torsion bar spring 40 or torsion-coil spring 60.
At least one equilibrium block of offsetting the unbalance mass, that the rotation due to two groups of eccentric parts and piston produces possesses in bent axle 10a.
When the rotor 30 of motor 3 is with dynamic crankshaft 10a to rotate, two eccentric parts drive corresponding piston to carry out eccentric rotary with pressurized gas respectively, so bent axle 10a produces axle moment sharply, because moment damping device makes bent axle 10a and rotor 30 carry out rotational slide, moment damping device has relaxed the variation of this axle moment, the angular velocity of rotor 30 is stablized, therefore can reduce the rotary vibration of rotary compressor 1.The equilibrium block possessed in bent axle 10a can offset the unbalance mass, that the rotation due to two groups of eccentric parts and piston produces.
According to the rotary compressor 1 of the embodiment of the present invention, by being provided with moment damping device, the rotary vibration of rotary compressor 1 can be reduced, simultaneously by being provided with the equilibrium block of the unbalance mass, of the rotation generation for offsetting eccentric part and piston on bent axle 10a, even if therefore the angle of swing of rotor 30 changes, method linearly coupled also can not increase.
In specific embodiments more of the present invention, within the scope of the rotational slide of bent axle 10a, possess groove main shaft 11 being carried out to path, in brief, a part for main shaft 11 attenuates to be formed as thin journal axle 12, thus can improve slippage loss.
In some embodiments of the invention, within the scope of the rotational slide of bent axle 10a, possesses the thin-walled portion of the quality of the side reducing bent axle 10a.That is, bent axle 10a is provided with the main shaft cutting portion 12a reducing bent axle 10a quality, more specifically, main shaft cutting portion 12a is located in thin journal axle 12, and wherein main shaft cutting portion 12a can be restricted to the equilibrium block of the unbalance mass, that the rotation for offsetting eccentric part and piston produces.
According to some embodiments of the present invention, the axial end of main shaft 11 is also provided with the axle head equilibrium block 36 for offsetting unbalance mass.
In some embodiments of the invention, rotor 30 is also provided with the rotor balance 38 for offsetting unbalance mass, wherein rotor balance 38 is arranged on the end face away from eccentric part 13 of rotor 30.
In order to avoid causing the increase of method linearly coupled owing to arranging rotor balance 38, in further embodiment of the present invention, by the reference line A-C1 in the center of gravity of unbalance mass, and the axle center of eccentric part 13, be θ with the angle of the equilibrium block center of gravity line B1-B1 in the axle center by rotor balance center of gravity and rotor 30, it is scope from 3 degree to 90 degree that rotor 30 starts front θ, in the sense of rotation of rotor 30, the center of gravity line of rotor balance 38 is positioned at after reference line.
The rotary compressor according to the several specific embodiment of the present invention is described in detail below with reference to Fig. 1-Figure 13.
Embodiment 1
The present embodiment is relevant to the application of the single cylinder rotary compressor using unidirectional induction machine.The motor 3 that rotary compressor 1 shown in Fig. 1 is configured by compressing mechanism 5 fixing in the cylindrical housings 2 sealed, its top forms, and stator 4 is fixed in housing 2.Rotor 30 has the feature with main shaft 11 rotational slide of compressing mechanism 5.
Be configured with torsion bar spring 40 in the axle mesopore 11a of the present embodiment in the main shaft 11 of bent axle 10, C motion end 46 that its two ends possess is connected with bent axle 10 and rotor 30 respectively with R motion end 45, bent axle 10 and rotor 30 carry out rotational slide.
The piston 21 being undertaken driving by the eccentric part 13 possessed in bent axle 10 carries out off-centre operation, pressurized gas, so bent axle 10 produces axle moment sharply.Torsion bar spring 40 has relaxed the variation of this axle moment, and the angular velocity of rotor 30 is stablized.Therefore, rotary compressor 1 can reduce rotary vibration.
Fig. 2 be bent axle 10 component figure, represent that unbalance mass, that eccentric part 13 and piston 21 produce is in the internal-neutralized design of bent axle 10.And, the sectional view that the planimetric map that the left figure of Fig. 3 is the bent axle 10 seen from countershaft end, right figure are thin journal axle 12.Bent axle 10 is formed by main shaft 11, eccentric part 13, countershaft 14, is possessed countershaft equilibrium block 15 between eccentric part 13 and countershaft 14.
In Fig. 2, the center of gravity G1 of countershaft equilibrium block 15 is the direction contrary with the center of gravity G0 of eccentric part 13.In the thin journal axle 12 that the part of main shaft 11 attenuates, possesses main shaft cutting portion 12a in above-mentioned center of gravity G0 side.And, possess axle mesopore 11a in the axle of main shaft 11, also have the cross-drilled hole 11d at right angles through with it.In addition, main shaft cutting portion 12a is called thin-walled portion.
The position of thin journal axle 12, carrying out in the scope of rotational slide with the pipe 35 that possesses in the axle center of rotor 30 described later, its working depth only has below 0.1mm.That is, thin journal axle 12 not only can shorten that the slip of main shaft 11 and pipe 35 is long improves slippage loss, also has the effect of the grinding deteriorated accuracy of the additional main shaft 11 that can produce avoided due to main shaft cutting portion 12a.And G2 is the center of gravity of the thin journal axle 12 possessing main shaft cutting portion 12a.
The centrifugal force that the rotation of total unbalance mass, of eccentric part 13 and piston 21 brings is F0, the centrifugal force of countershaft equilibrium block 15 and thin journal axle 12 is respectively F1 and F2.In addition, center of gravity G0 is respectively m and n to the size between center of gravity G1 and G2.Its result,
F0+F1+F2＝0····(1)
MF1=nF2 (2) sets up.
In addition, formula (2) balance that is moment of inertia.According to this formula, determine centrifugal force F1 and F2.
Above-mentioned 2 formula are set up, and in principle, method linearly coupled is zero.But, in rotor 30, there is no unbalance mass.In addition, when adding other components as the unbalance mass, of bent axle 10, or the processing beyond additional main shaft cutting portion 12a, need to revise above-mentioned formula.
The present embodiment is by shortening the size of eccentric part 13 and countershaft equilibrium block 15, and the quality of countershaft equilibrium block 15 can become large, but can have by the quality of ratio m/n, F2 the effect significantly reduced.Therefore, main shaft cutting portion 12a can substitute equilibrium block.That is, compare with not having the conventional art of countershaft equilibrium block 15, the present embodiment there is no need to configure equilibrium block in piston 30.And the sectional shape of main shaft cutting portion 12a is not limited to the shape shown in Fig. 3, can purport according to the present invention changes.
Fig. 4 represents compressing mechanism 5.The countershaft equilibrium block 15 rotated together with bent axle 10 has been received in the counter balance pocket 27a of the central diaphragm 27 possessed between cylinder 20 and supplementary bearing 26.The torsion bar spring 40 possessed in the axle mesopore 11a of bent axle 10, by turning round R motion end 45 that axle 41 and its two ends possess and C motion end 46 forms.Respective motion end is combined with rotor 30 and bent axle 10 in next procedure.
Fig. 5 represents the state of assemble rotor 30 in compressing mechanism 5.The present embodiment possesses pipe 35 in the internal diameter of rotor 30.Usually, hot jacket assembling is carried out to the external diameter of pipe 35 and the internal diameter of rotor 30.Thereafter, grinding is carried out to the internal diameter of pipe 35.
By R moment rod 43, after the end of pipe 35 and R motion end 45 combine, main shaft cutting portion 12a is accommodated in pipe 35.The moment of rotor 30, is delivered in bent axle 10 by R moment rod 43 and torsion bar spring 40.
At this moment, with being in proportion of the axle moment of bent axle 10, torsion bar spring 40 increases torsion angle.Thereafter, axle moment reduces, and recovers torsion angle.The action of this torsion angle is exactly axle moment pooling feature, the angular velocity of rotor 30 is stablized, reduces rotary vibration.In addition torsion bar spring 40 not still moment buffering, also can support rotor 30.
The difference of the bent axle 10 produced in 1 turn of rotor 30 and the angle of rotation of rotor 30 is phase angle, suitable with the windup-degree of torsion bar spring 40.Therefore, phase angle is mainly decided by the design of torsion bar spring 40 and the torque difference of bent axle 10 and rotor 30 and is increased and decreased.Usually, the maximum value at phase angle is everlasting less than 120 degree.
Fig. 6 represents the alternate design case of the above-mentioned countershaft equilibrium block 15 installing countershaft end equilibrium block 18 in the end of countershaft 14.After countershaft end equilibrium block 18 is integrated with bent axle 10, supplementary bearing 26 just can not have been installed, so after supplementary bearing 26 assembles, at the end winding support of countershaft 14 at screw.Thereafter, silencing apparatus 26a is secured in supplementary bearing 26.Like this, countershaft end equilibrium block 18 can reach equal effect as the substitute of countershaft equilibrium block.
Embodiment 2
Embodiment illustrated in fig. 72 is alternate design of main shaft cutting portion 12a, is fixed after the periphery of the opening slot 11b that the axle head of main shaft 11 possesses inserts axle head equilibrium block 36 by C shelves ring 39.Opening slot 11b, R moment rod 43, together with R motion end 45, is rotatable gap, above-mentioned phase angle.Embodiment 2 compared with embodiment 1, the configuration sized n of axle head equilibrium block 36 can be longer, so the quality of F2 can be little, forms miniaturization.
In addition, the gap of opening slot 11b, as the spacing use of torsional amplitude determining torsion bar spring 40, can be applied flexibly as the means of maximum value at the phase angle determining bent axle 10 and rotor 30.In addition, axle head equilibrium block 36 and main shaft cutting portion 12a can share.
Embodiment 3
Embodiment illustrated in fig. 83, be the alternate design of the main shaft cutting portion 12a used in embodiment 1, and designed the same in the past, the rotor balance 38 of little shape light weight be installed in the end ring 32a of rotor 30.But rotor balance 38 is rotated together with rotor 30, change in the scope at above-mentioned phase angle.Therefore, due to the variation of centrifugal force F2, there is invalid problem formula (1) and (2), and normal vibration can increase.
This problem and solve scheme are described by Fig. 9.The reference line A of the unbalance mass, of above-mentioned bent axle 10, be the straight line A-C1 in axle center by bent axle 10 or rotor 30.
In addition, the maximum value at phase angle be 2 θ (90 degree), rotor 30 rotate to be counterclockwise direction.First, illustrate as problem, according to design basis in the past, the line of reference line A makes the center of gravity G3 of equilibrium block consistent.
Rotor 30 starts, and after turning around, center of gravity G3 rotates the angular movement of 2 θ counter clockwise to C2, get back to C1 afterwards from C1.That is, this design is when rotor 30 1 turns, and the variation of equilibrium block is degree (C2) → 180,180 degree of (C1) → 270 degree (C1).In this variation, the maximum angular of equilibrium block vector is 270 degree (C2).
On the other hand, the present embodiment, rotate clockwise direction on the line of the straight line B1-B1 of angle θ from reference line A, make the center of gravity G3 of rotor balance 38 consistent.At this moment, the position of center of gravity G3 is the angle of 180 degree of-θ=135 degree from reference line A.Rotor 30 starts after 1 turn, and center of gravity G3 by maximum rotation 2 θ of counter clockwise direction, moves to B2 from B1.Thereafter B1 is got back to.
This gimmick is by the method for phase angle 2 θ bis-points centered by reference line A.Therefore, rotor balance about 38 swings on an equal basis.Namely 135% (B1) → 180% (C1) → 225% (B2) → 180% (C1) → 135% (B1) changes like this.The maximum angular of equilibrium block vector be at this moment 135 degree (B1) with 225 degree (B2), compared with design basis in the past, equilibrium block vector maximum angle will lack 45 degree.Therefore, affecting aspect the present embodiment and can significantly reduce on method linearly coupled.
Conclusion: the maximum value at above-mentioned phase angle is 2 θ, before the startup of rotor 30, the center of gravity angle of rotor balance 38 is just passable relative to the design of eccentric part 13, postponement θ.But phase angle can significantly change according to operating conditions, so determine that the scope at phase angle is more difficult in the design phase.Therefore, above-mentioned θ is the scope of 3 ~ 90 degree, can confirm to decide optimum value by actual compressor.
Embodiment 4
The 1 group of eccentric part received in the countershaft side compression chamber of the countershaft equilibrium block 15 illustrated in above-described embodiment or countershaft end equilibrium block 18 and twin-tub rotation-type compressor is suitable with piston.Therefore, the present invention can be applied in twin-tub rotation-type compressor.
Embodiment 4 shown in Figure 10 represents the ssembly drawing of compressing mechanism 5a and rotor 30 in twin-tub rotation-type compressor.2 the eccentric part 13a and eccentric part 13b that arrange by 180 degree of opposite directions are possessed in bent axle 10a.In each compression chamber of 2 cylinder 20a and cylinder 20b, receive piston 21a by above-mentioned crank-driven and piston 21b.Therefore, these are unbalance mass, A1 of producing of bent axle 10a and unbalance mass, A2, these are the differential seat angle of 180 degree.
Here, the gross mass of unbalance mass, A1 and A2, the gross mass being respectively eccentric part 13a and piston 21a, eccentric part 13b and piston 21b.This, unbalance mass, A1 > unbalance mass, A2, be provided with less of poor quality like this.As these means, quality can be changed between 2 pistons or 2 bent axles.
In the present embodiment, several pore 13c that can add through eccentric part 13b carry out lightweight to eccentric part 13b.And identical with embodiment 1, add the main shaft cutting portion 12a as equilibrium block in main shaft 11, above-mentioned formula (1) and (2) can be set up.Therefore, the designing technique disclosed from embodiment 1 to 4 can be applied in twin-tub machine.
Embodiment 5
The illustrated the present embodiment of Figure 11 is the cases of design that alternative torsion bar spring 40 uses torsion-coil spring 60.Torsion-coil spring 60, to be made up of the R motion end 65 at coil portion 61 and its two ends and C motion end 66.
Figure 12 installs C motion end 66 and R motion end 65 installation diagram respectively in the axle head of bent axle 10 and the end ring groove 32c of rotor 30.Figure 13 is the planimetric map from the Figure 12 viewed from the upper end side of rotor 30.
Even this represents that the present embodiment uses the design of twist coil spring 60, the design techniques disclosed from upper note embodiment 1 to 3 also can be applied.
At this, the effect of the present invention disclosed from above-described embodiment 1 to embodiment 5 is described.
1, there is no need to configure equilibrium block in the rotor as in the past, so following effect can be obtained.
(1) by moment buffer method, more difficult whirling vibration can be reduced.In principle, the vibration of rotary compressor can significantly reduce.
(2) because there is no equilibrium block in rotor, so the upset effect of exhaust declines.Its result, can decline from housing oiling out.
(3) when high speed operation, the spindle deformation brought due to rotor balance quality can not be produced, so the reliability of bent axle and slippage loss can improve.
(4) equilibrium block of nonmagnetic substance that brass etc. is more expensive is not needed to use, so can reduce costs.
2, compared with DC motor waveform synthesis method, apply in all motors that the present invention can adopt in rotary compressor.
3, structure and simplicity of design, when the application of this rotary compressor, do not need special control.
4, not still in vertical rotating formula compressor, be also can apply in the low pressure rotary compressor of low pressure at horizontal rotary compressor, enclosure interior pressure.
The present invention's not still induction machine, also can apply in the variable-frequency type motor of variable speed.These compressors are mounted in air conditioner, refrigerating device, water heater, vehicle-mounted freezing air conditioner equipment etc.
In sum, one of them technical problem to be solved by this invention is: the bent axle and the rotor that possess the eccentric part making to have driven plunger carry out rotational slide, connect the reduction vibration mode of the moment damping device of these bent axles and rotor, due to the change of rotor angle of swing, normal vibration can change with the angle of equilibrium block, so can increase.
Solve wherein a kind of means of above-mentioned problem:
Equilibrium block is not set in the rotor, between eccentric part 13 and countershaft 14, is provided with countershaft equilibrium block 15, and possess thin-walled portion in the outer radius of main shaft 11.Their total centrifugal force balances with the unbalance mass, centrifugal force of the eccentric part 13 rotated at compression chamber 20a and piston 21.Therefore, even if the change of rotor angle of swing, method linearly coupled also can not increase.
Effect by adopting above-mentioned technological means to bring:
Rotary vibration and the method linearly coupled of rotary compressor can be reduced simultaneously.This vibration reduces the form that technology is applicable to all rotary compressors, and all motors adopted in them.In addition, bad impact is not had on electric efficiency, so can apply in wider operating conditions.In addition, control technique need not be added in the system of carrying.
In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score can be that the first and second features directly contact, or the first and second features are by intermediary mediate contact.And, fisrt feature second feature " on ", " top " and " above " but fisrt feature directly over second feature or oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " can be fisrt feature immediately below second feature or tiltedly below, or only represent that fisrt feature level height is less than second feature.
In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can combine in one or more embodiment in office or example in an appropriate manner.In addition, when not conflicting, the feature of the different embodiment described in this specification or example and different embodiment or example can carry out combining and combining by those skilled in the art.
Although illustrate and describe embodiments of the invention above, be understandable that, above-described embodiment is exemplary, can not be interpreted as limitation of the present invention, and those of ordinary skill in the art can change above-described embodiment within the scope of the invention, revises, replace and modification.
Claims (9)
1. a rotary compressor, is characterized in that, comprising:
There is the motor of stators and rotators;
The bent axle formed by main shaft, eccentric part and countershaft order of rotational slide is carried out with described rotor;
By the piston that described eccentric part drives;
Connect the moment damping device of described rotor and described bent axle respectively;
At least one equilibrium block of offsetting the unbalance mass, that the rotation due to described eccentric part and described piston produces possesses in described bent axle.
2. rotary compressor according to claim 1, is characterized in that, described rotary compressor is twin-tub rotation-type compressor, and the unbalance mass, that the rotation due to eccentric part described in two groups and piston produces offset by described equilibrium block.
3. rotary compressor according to claim 1, is characterized in that, described equilibrium block is located between described eccentric part and described countershaft or in the axial end portion of described countershaft.
4. rotary compressor according to claim 1 and 2, is characterized in that, described moment damping device is torsion bar spring or torsion-coil spring.
5. rotary compressor according to claim 1 and 2, is characterized in that, within the scope of the rotational slide of described bent axle, possesses the groove described main shaft being carried out to path.
6. rotary compressor according to claim 1 and 2, is characterized in that, within the scope of the rotational slide of described bent axle, possesses the thin-walled portion of the quality of the side reducing described bent axle.
7. rotary compressor according to claim 1 and 2, is characterized in that, the axial end of described main shaft is also provided with the axle head equilibrium block for offsetting described unbalance mass.
8. rotary compressor according to claim 1 and 2, is characterized in that, described rotor is also provided with the rotor balance for offsetting described unbalance mass.
9. rotary compressor according to claim 8, is characterized in that,
By the reference line in the center of gravity of described unbalance mass, and the axle center of described eccentric part, be θ with the angle of the equilibrium block center of gravity line in the axle center by described rotor balance center of gravity and described rotor, before described rotor startup, θ is the scope from 3 degree to 90 degree, in the sense of rotation of described rotor, the center of gravity line of described rotor balance is positioned at after described reference line.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510152074.1A CN104806526B (en) | 2015-04-01 | 2015-04-01 | Rotary compressor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510152074.1A CN104806526B (en) | 2015-04-01 | 2015-04-01 | Rotary compressor |
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| CN104806526A true CN104806526A (en) | 2015-07-29 |
| CN104806526B CN104806526B (en) | 2017-03-01 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108087282A (en) * | 2017-11-20 | 2018-05-29 | 珠海凌达压缩机有限公司 | Pump body and compressor |
| CN114183359A (en) * | 2021-12-08 | 2022-03-15 | 珠海凌达压缩机有限公司 | Vibration reduction assembly, pump body assembly and double-cylinder compressor |
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| JPH11230073A (en) * | 1998-02-10 | 1999-08-24 | Sanyo Electric Co Ltd | Compressor |
| US20120068559A1 (en) * | 2010-09-20 | 2012-03-22 | Denso Corporation | Rotating shaft support apparatus and magnetic motor having the same |
| EP2594797A2 (en) * | 2011-11-18 | 2013-05-22 | Kabushiki Kaisha Toyota Jidoshokki | Compressor for vehicle |
| CN204532830U (en) * | 2015-04-01 | 2015-08-05 | 广东美芝制冷设备有限公司 | Rotary compressor |
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2015
- 2015-04-01 CN CN201510152074.1A patent/CN104806526B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11230073A (en) * | 1998-02-10 | 1999-08-24 | Sanyo Electric Co Ltd | Compressor |
| US20120068559A1 (en) * | 2010-09-20 | 2012-03-22 | Denso Corporation | Rotating shaft support apparatus and magnetic motor having the same |
| EP2594797A2 (en) * | 2011-11-18 | 2013-05-22 | Kabushiki Kaisha Toyota Jidoshokki | Compressor for vehicle |
| CN204532830U (en) * | 2015-04-01 | 2015-08-05 | 广东美芝制冷设备有限公司 | Rotary compressor |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108087282A (en) * | 2017-11-20 | 2018-05-29 | 珠海凌达压缩机有限公司 | Pump body and compressor |
| CN108087282B (en) * | 2017-11-20 | 2020-09-22 | 珠海凌达压缩机有限公司 | Pump body and compressor |
| CN114183359A (en) * | 2021-12-08 | 2022-03-15 | 珠海凌达压缩机有限公司 | Vibration reduction assembly, pump body assembly and double-cylinder compressor |
| CN114183359B (en) * | 2021-12-08 | 2023-08-18 | 珠海凌达压缩机有限公司 | Vibration reduction assembly, pump body assembly and double-cylinder compressor |
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| Publication number | Publication date |
|---|---|
| CN104806526B (en) | 2017-03-01 |
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