CN203272137U - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- CN203272137U CN203272137U CN 201320217833 CN201320217833U CN203272137U CN 203272137 U CN203272137 U CN 203272137U CN 201320217833 CN201320217833 CN 201320217833 CN 201320217833 U CN201320217833 U CN 201320217833U CN 203272137 U CN203272137 U CN 203272137U
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- bent axle
- axial portion
- rotary compressor
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- demarcation strip
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Abstract
The utility model provides a rotary compressor which enables the eccentricity of an eccentric shaft part of a crankshaft to be increased and enables the maximal volume of a compression chamber to be enlarged, cannot lower the assembly property, can prevent refrigerants from being leaked, and can improve the compression efficiency. The rotary compressor drives a pair of compression mechanism parts (10a, 10b) superposed through clamping a baffle plate (30) by utilizing two eccentric shaft parts (51a, 51b); the crankshaft is provided with shaft parts (52a, 52b) which are supported respectively by end plates at two sides, and are formed respectively with different outer diameters; eccentric shaft parts (51a, 51b) of the crankshaft are formed respectively with different outer diameters; the inner diameter of a central through hole (33) of the baffle plate (30) is less than any of the outer diameters of the eccentric shaft parts (51a, 51b), and the baffle plate (30) is separated so as to surround a baffle plate insertion part (53) of the crankshaft (50).
Description
Technical field
The utility model relates to rotary compressor, a plurality of cylinders is particularly arranged, configuring the rotary compressor of demarcation strip between cylinder.
Background technique
The press part that rotary compressor has seal container (below be called " housing "), be configured in drive portion in housing (below be called " motor ") and driven by motor, be cooled at press part through sucking the next refrigeration agent of pipe arrangement supply, be discharged to outside housing through discharging pipe arrangement.This rotary compressor is used for refrigerating box, household freezer, air conditioner, water heater etc., so, require high capacity and cost degradation.
The press part of the rotary compressor of single cylinder have circular cylinder, circular rotary-piston, can be towards blade, spring, bent axle and a pair of end plate of the direction advance and retreat of the central shaft of cylinder.Circular cylinder configuration is carried out eccentric rotary in the interior perimembranous of cylinder.Blade is configured in the blade groove that is formed on cylinder.Spring pushes the direction of blade towards the central shaft of cylinder.Bent axle is formed be used to the eccentric axial portion that makes the rotary-piston eccentric rotary.A pair of end plate is rotatably mounted with bent axle, and the both ends of the surface of inaccessible cylinder.
Therefore, by the outer circumferential face of the inner peripheral surface of cylinder, rotary-piston and a pair of end plate formed space, be divided into a pair of space that volume increases and decreases respectively (below be called " pressing chamber ") by the blade of eccentric rotary with being divided into two.That is, formed refrigeration agent that the phase place that gradually increases at volume is attracted in the compressed mechanism of phase place that volume reduces gradually.
In addition, the press part of the rotary compressor of twin-tub, the above-mentioned structure (identical with compression mechanical part) that is equivalent to the rotary compressor of single cylinder is configured to 2 layers (2 grades), blade groove both is configured in the opposite phase of 180 °, between cylinder both, configuring by " demarcation strip " with replacing end plate.That is, bent axle has and is formed on 180 ° of rightabout a pair of eccentric axial portion, runs through the center through hole that is formed on demarcation strip, and rotatably mounted by a pair of end plate.
At this moment, the internal diameter of center through hole roughly is equivalent to the aggregate values (saying exactly, slightly larger than aggregate values) of offset of a pair of eccentric axial portion of bent axle.
Usually, in having 2 rotary compressors with upper cylinder half, when wanting to strengthen the maximum volume of pressing chamber, following three kinds of methods are arranged.That is, (1) increases cylinder the method for (axle direction lengthening).(2) cylinder bore is strengthened the method for (radial direction increasing).(3) method that the offset of the eccentric axial portion of bent axle is strengthened.
In the situation that (1) or (2), compressor can maximize, expensiveization.Therefore, in order to eliminate expensiveization that maximizes and bring, usually adopt the method for (3).
But, as previously mentioned, when the offset of the eccentric axial portion of bent axle increases, the internal diameter that is formed on the center through hole on demarcation strip also will increase, so, in (3), thus the pressing chamber that can produce adjacent cylinder via the large center through hole of internal diameter the problem of the generation that is interconnected " leakage stream ", compression efficiency variation.
For this reason, in the rotary compressor with 2 cylinders, in order not produce problem as described above, as the method that improves compressor efficiency, following scheme has been proposed: external diameter, the diameter of axle of setting independently respectively the eccentric axial portion of bent axle, demarcation strip is become the size that the eccentric axial portion of only having the path side can be passed through, thereby the leakage stream is reduced, reduce the slippage loss (for example referring to patent documentation 1) that brings with the oily viscosity of bearing.
Patent documentation 1: Japanese kokai publication hei 5-99171 communique
The model utility content
But there is following problem in the disclosed model utility of patent documentation 1.
In the structure of patent documentation 1 record, due to can only be from the eccentric axial portion of the path side of bent axle by demarcation strip, so, the assembling trouble.Namely, when the compression mechanical part of assembling demarcation strip and the eccentric axial portion that contains the path side, after wanting first the eccentric axial portion of path side to be passed the center through hole of demarcation strip, again circular rotary-piston is inlaid on this eccentric axial portion, then, setting-in the eccentric axial portion of this rotary-piston to be assembled into the cylinder of this path side indoor, then with the cylinder of large footpath side and the cylinder of above-mentioned path side, demarcation strip is clamped, under this state, fixing together with the end of bolt and both sides.Therefore, exist the many problems of assembling procedure.
In addition, when the method for utilizing (3) increases the maximum volume of pressing chamber, because the external diameter of the eccentric axial portion of bent axle increases, so the internal diameter of demarcation strip also must increase.If be set as certain above offset, can not guarantee the seal length of rotary-piston and demarcation strip, the pressing chamber of adjacent cylinder is interconnected and can produces " leakage stream ", thus the compression efficiency variation.
The utility model is made in order to address the above problem, the rotary compressor that its objective is the offset that a kind of eccentric axial portion that makes bent axle is provided to increase and the volume of pressing chamber is increased, this rotary compressor can not reduce assembling performance, can prevent refrigrant leakage simultaneously, can improve compression efficiency.
Rotary compressor of the present utility model, the bent axle that utilization has 2 eccentric axial portion drives and clips the stacked a pair of compression mechanical part of demarcation strip, this bent axle has respectively the axial region by the end plate supporting of both sides, wherein, the axial region of bent axle forms with different external diameters respectively, and the eccentric axial portion of bent axle forms with different external diameters respectively; The internal diameter of the center through hole of demarcation strip forms all littlely than any of the external diameter of the eccentric axial portion of bent axle, and demarcation strip is divided to surround the demarcation strip insertion part of bent axle.
In rotary compressor of the present utility model, preferably, the axial region of the path side of above-mentioned bent axle and the eccentric axial portion of path side are adjacent to configuration, and the eccentric axial portion of the axial region of the large footpath side of above-mentioned bent axle and large footpath side is adjacent to configuration.
In rotary compressor of the present utility model, preferably, the external diameter of the axial region of the path side of above-mentioned bent axle is more than 0.8 times and below 0.9 times of external diameter of the axial region of large footpath side.
In rotary compressor of the present utility model, preferably, the external diameter of the eccentric axial portion of the path side of above-mentioned bent axle is more than 0.86 times and below 0.94 times of external diameter of the eccentric axial portion of large footpath side.
In rotary compressor of the present utility model, preferably, the external diameter of the eccentric axial portion of the path side of above-mentioned bent axle is 0.925 times of external diameter of the eccentric axial portion of large footpath side.
Rotary compressor of the present utility model, the axial region of bent axle form with different external diameters respectively, and, the eccentric axial portion of bent axle forms with different external diameters respectively, the internal diameter of the center through hole of demarcation strip forms all littlely than any of the external diameter of the eccentric axial portion of bent axle, and demarcation strip is divided to surround the demarcation strip insertion part of bent axle, thus, can realize high capacity and cost degradation, and, can guarantee the seal length of rotary-piston, prevent refrigrant leakage, improve compression efficiency.
Description of drawings
Fig. 1 means the sectional side view of integral body of the rotary compressor of the utility model mode of execution 1.
Fig. 2 means the partial side sectional view of the compression mechanical part of rotary compressor shown in Figure 1.
Fig. 3 mean rotary compressor shown in Figure 1 compression mechanical part overlook part sectioned view.
Fig. 4 means the plan view of the demarcation strip of rotary compressor shown in Figure 1.
Fig. 5 means the figure of the running efficiency of rotary compressor shown in Figure 1.
The explanation of reference character
10a... the 1st compression mechanical part, 10b... the 2nd compression mechanical part, 11a... the 1st cylinder, 11b... the 2nd cylinder, 12a... the 1st piston, 12b... the 2nd piston, 13a... the 1st blade groove, 13b... the 2nd blade groove, 14a... the 1st blade, 14b... the 2nd blade, 15a... the 1st spring, 15b... the 2nd spring, 20a... the 1st end plate, 20b... the 2nd end plate, 25a... the 1st bearing, 25b... the 2nd bearing, 30 ... demarcation strip, 31... the 1st cuts apart shim, 32... the 2nd cuts apart shim, 33... center through hole, 34... parting plane, 40a... space, 40b... space, 50... bent axle, 51a... the 1st eccentric axial portion, 51b... the 2nd eccentric axial portion, 52a... the 1st bearing insertion part, 52b... the 2nd bearing insertion part, 53... demarcation strip insertion part, 60a... assembling bolt, 60b... assembling bolt, 71... assembling lag bolt, 72... assembling stay bolt, 100... rotary compressor (compressor), 101... housing, 101a... upper body, 101b... lower case, 102... motor, 102a... stator, 102b... rotor, 103... press part, 104... glass terminal, 105... discharge tube, 106a... the 1st suction pipe, 106b... the 2nd suction pipe, 107... absorbing silencer.
Embodiment
[mode of execution 1]
Below, with reference to accompanying drawing, the rotary compressor of the utility model mode of execution 1 is described.
Fig. 1～Fig. 4 schematically illustrates the rotary compressor of the utility model mode of execution 1.Fig. 1 means the sectional side view of the integral body of rotary compressor.Fig. 2 means the partial side sectional view of the compression mechanical part of rotary compressor.Fig. 3 mean rotary compressor compression mechanical part overlook part sectioned view.Fig. 4 means the plan view of the demarcation strip of rotary compressor.Each figure is all that schematically the utility model is not limited to illustrated mode.
In Fig. 1～Fig. 4, the driving source that rotary compressor 100 has housing 101 as seal container, be configured in housing 101 inside is drive portion (below be called " motor ") 102 and the press part 103 that is arranged on housing 101 inside.Below, describe the structure of each one in detail.
(housing)
On lower case 101b, the 1st suction pipe 106a and the 2nd suction pipe 106b that are fixed wtih motor 102, the 1st compression mechanical part 10a that consists of press part 103 and the 2nd compression mechanical part 101b and refrigeration agent are imported respectively the 1st compression mechanical part 10a and the 2nd compression mechanical part 10b.The 1st suction pipe 106a and the 2nd suction pipe 106b are connected with absorbing silencer 107, carry out the gas-liquid separation of refrigeration agent and removing of the dirt in refrigeration agent in absorbing silencer 107.
In the following description, to the identical content in the 1st compression mechanical part 10a and the 2nd compression mechanical part 10b, sometimes dispense " the 1st, the 2nd " and the footnote " a, b " of reference character that describe title.
(motor)
(press part)
The 1st compression mechanical part 10a has the 1st circular cylinder 11a, the 1st circular rotary-piston (below be called " the 1st piston ") 12a, the 1st blade 14a and the 1st spring 15a.The 1st piston 12a is configured in the interior perimembranous of the 1st cylinder 11a, on one side with the inner peripheral surface of the 1st cylinder 11a eccentric rotary on one side that joins.The 1st blade 14a can be configured in the 1st blade groove 13a that is formed on the 1st cylinder 11a towards the central axis direction of the 1st cylinder 11a with advancing and retreat.The 1st spring 15a is crimped on the 1st blade 14a the periphery of the 1st piston 12a.At this moment, the outer circumferential face of the 1st piston 12a is wire with the inner peripheral surface of the 1st cylinder 11a and contacts, and along with eccentric rotary, the contact position of wire moves at circumferencial direction.
Similarly, the 2nd compression mechanical part 10b has the 2nd circular cylinder 11b, the 2nd circular rotary-piston (below be called " the 2nd piston ") 12b, the 2nd blade 14b and the 2nd spring 15b.The 2nd piston 12b is configured in the interior perimembranous of the 2nd cylinder 11b, on one side with the inner peripheral surface of the 2nd cylinder 11b eccentric rotary on one side that joins.The 2nd blade 14b can be configured in the 2nd blade groove 13b that is formed on the 2nd cylinder 11b towards the central axis direction of the 2nd cylinder 11b with advancing and retreat.The 2nd spring 15b is crimped on the 2nd blade 14b on the periphery of the 2nd piston 12b.At this moment, the outer circumferential face of the 2nd piston 12b is wire with the inner peripheral surface of the 2nd cylinder 11b and contacts, and along with eccentric rotary, the contact position of wire moves at circumferencial direction.
In addition, the internal diameter of the internal diameter of the 1st piston 11a and the 2nd piston 11b is designed to equate.
(pressing chamber)
The pressing chamber of each compression mechanical part 10 is divided into two parts with the space of each cylinder chamber at Zhou Fangxiang with blade 14 and forms.Namely, at the 1st compression mechanical part 10a, top the 1st space 40a that surrounds by the following and demarcation strip 30 of the outer circumferential face of the inner peripheral surface of the 1st cylinder 11a, the 1st piston 12a, the 1st end plate 20a, by joining (roughly joining to wire) of the outer circumferential face of the inner peripheral surface of the 1st cylinder 11a and the 1st piston 12a and joining (roughly joining to wire) of the outer circumferential face of the 1st blade 14a and the 1st piston 12a, be split into two-part at Zhou Fangxiang.
At the 2nd compression mechanical part 10b, similarly, following the 2nd space 40b that surrounds by the following and demarcation strip 30 of the outer circumferential face of the inner peripheral surface of the 2nd cylinder 11b, the 2nd piston 12b, the 2nd end plate 20b, by joining of the outer circumferential face of the inner peripheral surface of the 2nd cylinder 11b and the 2nd piston 12b and joining of the outer circumferential face of the 2nd blade 14b and the 2nd piston 12b, be split into two-part (see figure 3) at Zhou Fangxiang.
(bent axle)
Bent axle 50 is configuring the 1st bearing insertion part 52a, demarcation strip insertion part 53 and the 2nd bearing insertion part 52b coaxially.Between the 1st bearing insertion part 52a and demarcation strip insertion part 53, formed the 1st eccentric axial portion 51a towards side's bias.Between the 2nd bearing insertion part 52b and demarcation strip insertion part 53, formed the 2nd eccentric axial portion 51b towards the opposing party's bias.
At this moment, the 1st eccentric axial portion 51a and the 2nd eccentric axial portion 51b be (eccentric direction differs 180 °) toward each other, the axis parallel of the central shaft of each eccentric axial portion 51 and bent axle 50.
In addition, the 1st bearing insertion part 52a is rotatably by the 1st bearing 25a supporting that is arranged at the 1st end plate 20a inner peripheral surface.The 2nd bearing insertion part 52b is rotatably by the 2nd bearing 25b supporting that is arranged at the 2nd end plate 20b inner peripheral surface.The center through hole 33 that is formed on demarcation strip 30 central authorities is run through in demarcation strip insertion part 53.
(compression of refrigeration agent)
The 1st eccentric axial portion 51a runs through the interior perimembranous of the 1st piston 12a, the 2nd eccentric axial portion 51b runs through the interior perimembranous of the 2nd piston 12b, so, utilize the rotation of bent axle 50, make the 1st piston 12a and the 2nd piston 12b differ eccentric rotary under the state of 180 ° of phase places (see (a) of Fig. 3 and (b)) with respect to the opposing party a side.
Therefore, by the rotation of bent axle 50, be split into the side space of two-part the 1st space 40a, volume increases gradually, is split into the opposing party space of two-part the 1st space 40a, and volume reduces gradually.That is, form the 1st suction port (not shown) in the position that is being equivalent to a side space, form the 1st exhaust port (not shown) in the position that is equivalent to the opposing party space, so, after refrigeration agent is inhaled into from the 1st suction port, compressed and discharge from the 1st exhaust port.
(demarcation strip)
As shown in Figure 4, demarcation strip 30 is to be formed with the roughly disk of center through hole in central authorities.The shape of demarcation strip 30 is general toroidal, along the parting plane 34 of radiation direction (parallel with the direction of the 2nd blade 14b advance and retreat with the 1st blade 14a), forms and is divided into the 1st with being divided into two and cuts apart the shape that shim 31 and the 2nd is cut apart shim 32.In addition, these the 1st are cut apart shim 31 and the 2nd and cut apart shim 32, in order at circumferencial direction, shim to be interconnected, have for example assembling with bolt 60a and 60b.In addition, as with the interconnective means of shim, also can adopt fastener to hook.In addition, parting plane 34 be equivalent to be formed on the 1st cut apart on shim 31 the 1st plane be formed on the 2nd and cut apart the face that the 2nd plane on shim 32 joins, but, for convenience of explanation, not only refer to the face that the 1st plane and the 2nd plane join, sometimes refer to the face separately on the 1st plane and the 2nd plane.In addition, for parting plane 34, the face that joins is not limited to the plane, has also comprised the step surface of mutual face contact.
(diameter of axle and aperture)
At this moment, with the axial region of bent axle 50, namely the 1st bearing insertion part 52a and the 2nd bearing insertion part 52b are set as respectively different external diameters, and, the 1st eccentric axial portion 51a and the 2nd eccentric axial portion 51b are set as respectively different external diameters.In addition, the internal diameter of the center through hole 33 of demarcation strip 30 forms all littlely than the external diameter of arbitrary eccentric axial portion 51a, the 51b of bent axle 50.Namely, as shown in Figure 2, be that the external diameter of d2, the 1st eccentric axial portion 51a is that the external diameter of dp1, the 2nd eccentric axial portion 51b is that the internal diameter of the center through hole 33 of dp2, demarcation strip 30 is when being dm if the external diameter of the 1st bearing insertion part 52a of bent axle 50 is the external diameter of d1, the 2nd bearing insertion part 52b, d1 ≠ d2, dp1 ≠ dp2, dm＜dp1, dp2.
In addition, in illustrated example, be d1〉d2, dp1〉dp2, dm＜dp2＜dp1.
In illustrated example, the eccentric axial portion (the 2nd eccentric axial portion 51b) of the axial region of the path side of bent axle 50 (the 2nd bearing insertion part 52b) and path side is adjacent to configuration, and the eccentric axial portion (the 1st eccentric axial portion 51a) of the axial region (the 1st bearing insertion part 52a) of large footpath side and large footpath side is adjacent to configuration.
As mentioned above, the axial region of bent axle 50 forms with different external diameters, simultaneously, eccentric axial portion forms with different external diameters, in addition, the internal diameter of the center through hole 33 of demarcation strip 30 is all less than any of the external diameter of eccentric axial portion, like this, can guarantee the seal length between the internal diameter of center through hole 33 of the external diameter of seal length between the internal diameter of center through hole 33 of the external diameter of the 1st piston 12a and demarcation strip 30 and the 2nd piston 12b and demarcation strip 30.Therefore, the pressing chamber of each cylinder 11a, 11b is not communicated with mutually, can prevent refrigrant leakage.So the offset that can realize the eccentric axial portion of bent axle 50 increases and the maximum volume increaseization of the pressing chamber that causes, can improve compression efficiency.
On the other hand, because the internal diameter of the center through hole 33 of demarcation strip 30 forms all littlely than any of the external diameter of eccentric axial portion, so, section of available following methods assemble compressible mechanism.
(1) the 1st bearing insertion part 52a of bent axle 50 is inserted the 1st end plate 20a, the 1st eccentric axial portion 51a and setting-in the 1st piston 12a thereon of large footpath side are assembled in cylinder 11a.Then, see Fig. 1 with assembling with lag bolt 71(), fastening fixing the 1st end plate 20a and the 1st cylinder 11a.Assembling method and the patent documentation 1 of the 1st compression mechanical part 10a hereto are roughly the same.
The shim 31,32 of respectively cutting apart of the demarcation strip 30 that (2) will cut apart with bolt 60a, 60b with assembling connects, with by the demarcation strip insertion part 53 of respectively being cut apart shim 31,32 encirclement bent axles 50.Like this, the demarcation strip insertion part 53 of bent axle 50 becomes the state of the center through hole 33 that runs through demarcation strip 30.
(3) the 2nd eccentric axial portion 51b of path side and setting-in the 2nd piston 12b thereon are assembled in the 2nd cylinder 11b.
(4) the 2nd bearing insertion part 52b of bent axle 50 is inserted the 2nd end plate 20b of path side, clipping under the state of demarcation strip 30 with the 1st cylinder 11a and the 2nd cylinder 11b, see Fig. 1 with assembling with stay bolt 72(), the 2nd end plate 20b, the 2nd cylinder 11b and the 1st cylinder 11a are tightened together.
In addition, the assembling that shows is the method for assembling to the order of path side (downside) according to from large footpath side (upside), but also can be conversely, and according to assembling to the order of large footpath side (upside) from path side (downside), which kind of method can.In addition, in superincumbent explanation, be that demarcation strip 30 is cut apart, but also can not cut apart demarcation strip 30 but at 53 places, demarcation strip insertion part, bent axle 50 is cut apart.
According to the assembling method of above-mentioned compression mechanical part, more not a halfpenny the worse than assembling method before, so, can suppress cost low.In addition, as product, the reliability of aspect of performance is more important than reducing assembly cost, as mentioned above, and owing to can prevent refrigrant leakage, so, the rotary compressor 100 that can obtain having high reliability.
In addition, the outside diameter d 2 of the axial region of the path side of bent axle 50 (the 2nd bearing insertion part 52b) preferably the axial region (the 1st bearing insertion part 52a) of large footpath side more than 0.8 times of outside diameter d 1, below 0.9 times.At this, the reason that lower limit is set as d2=0.8 * d1 is, if external diameter less than 0.8 times, can not be guaranteed rigidity, the intensity of axle, and with the reason that CLV ceiling limit value is set as d2=0.9 * d1 is, in order to strengthen the offset of eccentric axial portion 51a, 51b as far as possible.
In addition, the outside diameter d p2 of the eccentric axial portion of the path side of bent axle 50 (the 2nd eccentric axial portion 51b) is more than 0.86 times of outside diameter d p1 of the eccentric axial portion (the 1st eccentric axial portion 51a) of large footpath side, below 0.94 times, to be more preferably dp2 be more than 0.92 times of dp1, below 0.93 times.Especially, dp2=0.925 * dp1 is best suited for.
These numerical definitenesses obtain from experimental result, as described later, be according to shown in Figure 5 year running efficiency plotted curve determine.
[other mode of execution]
The above shows press part 103 by the 1st compression mechanical part 10a and the 2nd compression mechanical part 10b consist of, the eccentric axial portion of bent axle 50 is the path side and large footpath side is integrated structure.But the utility model is not limited thereto, and also can cut apart between the eccentric shaft with bent axle 50, during assembling, connects after being provided with demarcation strip 30 again and consists of compressing mechanism.
The improvement effect of running efficiency of the rotary compressor (two stage compressor) 100 of present embodiment is described at last.Fig. 5 represents the eccentric diameter of axle dp1 and the ratio of the eccentric diameter of axle dp2 of path side and the relation of running efficiency of the large footpath side of bent axle.Transverse axis represents the eccentric diameter of axle ratio of dp2/dp1, and the longitudinal axis represents a year running efficiency.
In addition, rotary compressor shown in Figure 5 is the rotary compressor of internal high pressure type.In Fig. 5, take the crankshaft eccentric diameter of axle of rotary compressor before than as 1 o'clock year running efficiency as benchmark (100%), represent the running efficiency of the compressor 100 of present embodiment.
For the running efficiency of the compressor 100 of present embodiment, when the eccentric diameter of axle dp2 of the path side of bent axle was 0.925 times of eccentric diameter of axle dp1 of large footpath side, maximum was about 102%, had improved approximately 2% running efficiency than before rotary compressor.
As can be seen from Fig. 5, when 0.86≤dp2/dp1≤0.94, running efficiency surpasses 101%.When 0.92≤dp2/dp1≤0.93, running efficiency surpasses 101.5%.
As can be known from the results, the lateral deviation axle footpath, large footpath by making bent axle and ratio (dp2/dp1) optimization in path lateral deviation axle footpath can suppress the frictional loss of rotary-piston and eccentric shaft, improve running efficiency.
Claims (5)
1. rotary compressor utilizes the bent axle with 2 eccentric axial portion to drive and clips the stacked a pair of compression mechanical part of demarcation strip, and this bent axle has respectively the axial region by the end plate supporting of both sides, it is characterized in that,
The axial region of above-mentioned bent axle forms with different external diameters respectively, and the eccentric axial portion of above-mentioned bent axle forms with different external diameters respectively;
The internal diameter of the center through hole of the above-mentioned demarcation strip that is run through by above-mentioned bent axle forms all littlely than any of the external diameter of the eccentric axial portion of above-mentioned bent axle, and above-mentioned demarcation strip is divided to surround the demarcation strip insertion part of above-mentioned bent axle.
2. rotary compressor as claimed in claim 1, is characterized in that, the axial region of the path side of above-mentioned bent axle and the eccentric axial portion of path side are adjacent to configuration, and the eccentric axial portion of the axial region of the large footpath side of above-mentioned bent axle and large footpath side is adjacent to configuration.
3. rotary compressor as claimed in claim 1 or 2, is characterized in that, the external diameter of the axial region of the path side of above-mentioned bent axle is more than 0.8 times and below 0.9 times of external diameter of the axial region of large footpath side.
4. rotary compressor as claimed in claim 1 or 2, is characterized in that, the external diameter of the eccentric axial portion of the path side of above-mentioned bent axle is more than 0.86 times and below 0.94 times of external diameter of the eccentric axial portion of large footpath side.
5. rotary compressor as claimed in claim 4, is characterized in that, the external diameter of the eccentric axial portion of the path side of above-mentioned bent axle is 0.925 times of external diameter of the eccentric axial portion of large footpath side.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-133846 | 2012-06-13 | ||
| JP2012133846A JP5781019B2 (en) | 2012-06-13 | 2012-06-13 | Rotary compressor |
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| Publication Number | Publication Date |
|---|---|
| CN203272137U true CN203272137U (en) | 2013-11-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310149258.3A Active CN103486040B (en) | 2012-06-13 | 2013-04-26 | Rotary compressor |
| CN 201320217833 Expired - Lifetime CN203272137U (en) | 2012-06-13 | 2013-04-26 | Rotary compressor |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201310149258.3A Active CN103486040B (en) | 2012-06-13 | 2013-04-26 | Rotary compressor |
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| Country | Link |
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| JP (1) | JP5781019B2 (en) |
| CN (2) | CN103486040B (en) |
| CZ (1) | CZ305876B6 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103486040A (en) * | 2012-06-13 | 2014-01-01 | 三菱电机株式会社 | Rotary compressor |
| CN106122019A (en) * | 2016-08-09 | 2016-11-16 | 珠海凌达压缩机有限公司 | A kind of rotary compressor |
| CN108061020A (en) * | 2018-01-08 | 2018-05-22 | 珠海凌达压缩机有限公司 | A kind of compressor disk structure, compressor and air conditioner |
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| CN104153993B (en) * | 2014-08-27 | 2017-06-30 | 郑州凌达压缩机有限公司 | Compressor roller, compressor pump and compressor |
| CN104314815B (en) * | 2014-09-22 | 2016-12-07 | 安徽美芝精密制造有限公司 | Multi-cylinder rotary compressor |
| CN108825500B (en) * | 2018-08-06 | 2024-03-29 | 珠海凌达压缩机有限公司 | Compressor pump body and rotary compressor with same |
| CN109236651B (en) * | 2018-10-11 | 2020-03-27 | 珠海格力电器股份有限公司 | Variable-capacity compressor and air conditioning system thereof |
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| JP3723408B2 (en) * | 1999-08-31 | 2005-12-07 | 三洋電機株式会社 | 2-cylinder two-stage compression rotary compressor |
| JP2003328972A (en) * | 2002-05-09 | 2003-11-19 | Hitachi Home & Life Solutions Inc | Sealed two-cylinder rotary compressor and manufacturing method thereof |
| JP5284210B2 (en) * | 2009-07-23 | 2013-09-11 | 三菱電機株式会社 | Rotary compressor, manufacturing method thereof, and manufacturing apparatus thereof |
| JP4897867B2 (en) * | 2009-11-20 | 2012-03-14 | 三菱電機株式会社 | Multi-cylinder rotary compressor and manufacturing method thereof |
| JP5341031B2 (en) * | 2010-06-30 | 2013-11-13 | 三菱電機株式会社 | Multi-cylinder rotary compressor, its assembling method and its manufacturing apparatus |
| JP5781019B2 (en) * | 2012-06-13 | 2015-09-16 | 三菱電機株式会社 | Rotary compressor |
-
2012
- 2012-06-13 JP JP2012133846A patent/JP5781019B2/en active Active
-
2013
- 2013-04-04 CZ CZ2013-260A patent/CZ305876B6/en not_active IP Right Cessation
- 2013-04-26 CN CN201310149258.3A patent/CN103486040B/en active Active
- 2013-04-26 CN CN 201320217833 patent/CN203272137U/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103486040A (en) * | 2012-06-13 | 2014-01-01 | 三菱电机株式会社 | Rotary compressor |
| CN103486040B (en) * | 2012-06-13 | 2016-07-27 | 三菱电机株式会社 | Rotary compressor |
| CN106122019A (en) * | 2016-08-09 | 2016-11-16 | 珠海凌达压缩机有限公司 | A kind of rotary compressor |
| CN106122019B (en) * | 2016-08-09 | 2018-06-08 | 珠海凌达压缩机有限公司 | A kind of rotary compressor |
| CN108061020A (en) * | 2018-01-08 | 2018-05-22 | 珠海凌达压缩机有限公司 | A kind of compressor disk structure, compressor and air conditioner |
| CN108061020B (en) * | 2018-01-08 | 2023-03-10 | 珠海凌达压缩机有限公司 | Compressor partition plate structure, compressor and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013256906A (en) | 2013-12-26 |
| CN103486040B (en) | 2016-07-27 |
| CN103486040A (en) | 2014-01-01 |
| CZ305876B6 (en) | 2016-04-20 |
| CZ2013260A3 (en) | 2014-03-12 |
| JP5781019B2 (en) | 2015-09-16 |
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