CN203463285U - Rotary compressor and refrigeration cycle device - Google Patents
Rotary compressor and refrigeration cycle device Download PDFInfo
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- CN203463285U CN203463285U CN201320481580.1U CN201320481580U CN203463285U CN 203463285 U CN203463285 U CN 203463285U CN 201320481580 U CN201320481580 U CN 201320481580U CN 203463285 U CN203463285 U CN 203463285U
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Abstract
The utility model provides a rotary compressor and a refrigeration cycle device with the rotary compressor. A motor part and a compression mechanism part connected with the motor part through a rotating shaft are contained in a closed shell, wherein the compression mechanism part comprises a cylinder, a roller, blades and a spiral spring; the cylinder is provided with a cylinder chamber; the roller makes eccentric motion in the cylinder chamber; the blades press against the roller, so that the cylinder chamber is divided into a compression side and a suction side; according to the spiral spring, the blades are elastically pressed for energizing in a mode of allowing the blades to press against the roller; the blades refer to two split blades which are overlapped in the height direction of the cylinder; the two split blades are pressed through the spiral spring; a contact part between the spiral spring and the split blades is provided with a joint sealing part which is larger than or equal to two circles; each split blade is provided with a spiral spring mounting groove comprising a conical part and a parallel part; the conical part is arranged from an end edge to the length direction; the parallel part is parallel to the joint sealing part of the spiral spring.
Description
Technical field
Mode of execution of the present utility model relates to a kind of rotary compressor and possesses described rotary compressor and form the freezing cycle device in freeze cycle (cycle) loop.
Background technique
The freezing cycle devices that possess rotary compressor that adopt more.In this kind of rotary compressor, be to link motor part and compression mechanical part via running shaft.In compression mechanical part, possess: cylinder (cylinder), forms cylinder chamber at inside diameter; In cylinder (roller) ， cylinder chamber, make eccentric motion; And blade (vane), be connected in cylinder ，Er Jiang cylinder chamber and be divided into compressed side and suction side.
Previously, as shown in Fig. 8 (A), with respect to 1 cylinder, possess 1 blade, the front end of blade is slidably connected to cylinder perisporium.Blade is to represent with following numerical expression (1) to the pressing force of cylinder (load) F.
F＝{Pd×(L1+L2)-(Pm×L1+Ps×L2)}×H……(1)
Pd: closed shell (case) internal pressure (=ejection pressure), L1: the projected length of the suction side of blade front end, L2: the projected length of the compressed side of blade front end, Ps: suction side pressure, Pm: the thickness (=blade height) of high pressure (compression) side pressure, H=cylinder.
Prior art document
Patent documentation
Patent documentation 1: No. 4488104 communique of Japan Patent
Model utility content
[problem that wish solves]
In this kind of existing structure, in the situation that the relatively little problem of the thickness of cylinder (axial length) is few, if but the thickness of cylinder becomes large, there is following shortcoming.
1) element precision becomes large to the inhomogeneity impact of the surface pressure of the slide part of blade front end and cylinder perisporium.The squareness of running shaft, (master) bearing and cylinder end face etc. worsens, thereby at slide part place, produces touch (circle) of the locality shown in Fig. 8 (B).
The load that blade is applied is proportionally to increase with cylinder thickness.Therefore, part touch part real surface pressure (contact force or pressing force) with following numerical expression (2), represent.
Pt＝Pa×H/Lt……(2)
Pt: real surface pressure, the Pa of part touched in part: average surface pressure, Lt: actual contact length.
That is, the load Pt that blade is applied is directly proportional and becomes very high to cylinder thickness H, can produce sintering or abnormal wear at the slide part place of cylinder and blade thus.
2) because the gas load that running shaft is applied increases, so the bending of running shaft becomes large.Thus, with above-mentioned 1) similarly, at slide part place, produce touching of locality, the surface pressure of slide part uprises and produces sintering or abnormal wear.
In order to prevent these problems, the slide part of blade and cylinder is carried out to special surface treatment, or adopt blade and cylinder are made as to the structure of one, but all can cause the rising of cost (cost).
Based on this kind of situation, expect a kind of rotary compressor and possess the freezing cycle device of described rotary compressor, described rotary compressor is by being divided into blade two, thereby alleviate the surface pressure of cutting apart the front end of blade and the slide part of cylinder, by being made as one by pressing the helical spring (coil spring) of cutting apart blade, even if depart from also and can prevent helical spring departing from towards glide direction thereby cut apart blade, suppress expensiveization without special sliding material.
[solving the means of problem]
In the rotary compressor of present embodiment, the compression mechanical part of accommodating motor part and linking with motor part via running shaft in closed shell, compression mechanical part comprises: cylinder, has cylinder chamber, in cylinder ， cylinder chamber, make eccentric motion, blade, is connected to cylinder and moves back and forth in ，Jiang cylinder chamber and be divided into compressed side and suction side, and helical spring, be connected to the rear end side of blade, the mode that is connected to cylinder with blade front end is energized towards cylinder direction to blade, blade is to be axially in the short transverse of cylinder at running shaft, overlapping configuration has two to cut apart blade, helical spring is cut apart the mode of blade and form to press two with a helical spring, and then, helical spring is possessing with the contact segment of cutting apart blade the portion of connecting airtight, cut apart blade and possess the helical spring mounting groove that comprises taper portion and parallel portion, described taper portion is from cutting apart blade end edge towards the setting of front end direction, described parallel portion be from described taper portion further forward end direction arrange continuously, and parallel with the vibration-direction of blade.
Described rotary compressor, wherein, when the length dimension of cutting apart the parallel portion of the helical spring mounting groove on blade described in being located at being made as to D, the described helical spring length dimension that connects airtight portion and being made as T, to meet the mode of following numerical expression, set: D < T.
Described rotary compressor, wherein, with form described helical spring mounting groove described parallel portion length direction quadrature, described in cut apart the shape of the width direction of blade, be equate with described helical spring internal diameter and external diameter circular-arc.
Described rotary compressor, wherein, with form described helical spring mounting groove described parallel portion length direction quadrature, described in to cut apart the shape of width direction of blade linearly, and be the width dimensions contacting with external diameter with described helical spring internal diameter.
The rotary compressor of present embodiment, wherein, in thering is the described rotary compressor of a plurality of cylinders, to described, cut apart the described helical spring that blade energizes and be only arranged in 1 cylinder in described a plurality of cylinder, described in possessing for cylinder described in other, cut apart blade, replace helical spring and external pressure in described closed shell as back pressure.
The rotary compressor of present embodiment, wherein, described freezing cycle device forms freeze cycle loop, and described freeze cycle loop is that described rotary compressor and condenser, expansion gear are communicated with via refrigerant pipe with vaporizer.
Accompanying drawing explanation
Fig. 1 is the sectional arrangement drawing of rotary compressor of present embodiment and the freeze cycle structural drawing of the summary of freezing cycle device.
Fig. 2 is the planimetric map of cylinder of the compression mechanical part of present embodiment.
Fig. 3 is the figure that the blade of the compression mechanical part of present embodiment and helical spring structure are described.
Fig. 4 (A), Fig. 4 (B) are the figure that spring fitting groove set on the blade of present embodiment and helical spring structure are described.
Fig. 5 (A), Fig. 5 (B) are the figure that the spring fitting groove of modified embodiment of the present embodiment is described.
Fig. 6 (A), Fig. 6 (B) are the figure that the spring fitting groove of the another variation of present embodiment is described.
Fig. 7 is the sectional arrangement drawing of compression mechanical part of the another variation of present embodiment.
Fig. 8 (A), Fig. 8 (B) are the figure first pre-structure of explanation, that blade is described with respect to the sliding motion structure of cylinder and the figure that touching of the locality of blade described.
Reference character:
1: closed shell
2: motor part
3: compression mechanical part
4: running shaft
5: cylinder
5A: the 1st cylinder
5B: the 2nd cylinder
6: middle demarcation strip
7: main bearing
8: supplementary bearing
9: cylinder
9a: the 1st cylinder
9b: the 2nd cylinder
10: cylinder chamber
10A: the 1st cylinder chamber
10B: the 2nd cylinder chamber
11,13: ejection baffler
12a, 12b: ejection valve system
15,40,70: blade
15A: the 1st blade
15B: the 2nd blade
16,50,80: helical spring
16a: connect airtight portion
17: blade groove
18: blade back chamber
19: spring accepting hole
20: condenser
21: expansion gear
22: vaporizer
23: liquid-storage container
25: suck and use hole
26: spraying hole
30,60,90: helical spring mounting groove
30a, 60a: taper portion
30b, 60b, 90b: parallel portion
A, b: cut apart blade
D: the length dimension of parallel portion
K, Ka: rotary compressor
L1: the projected length of the suction side of blade front end
L2: the projected length of the compressed side of blade front end
P: refrigerant pipe
Pd: closed shell internal pressure
Pm: high side pressure
Ps: suction side pressure
R: freeze cycle loop
S: helical spring wire diameter
Sa: the width dimensions of parallel portion
T: the length dimension that connects airtight portion
Embodiment
Below, based on accompanying drawing explanation present embodiment.
Fig. 1 is the summary sectional arrangement drawing of the rotary compressor K of two cylinder type, and is the structural drawing of freeze cycle loop R that possesses the freezing cycle device of described rotary compressor K.
First, from the rotary compressor K of two cylinder type, start to describe.
In figure, 1 is closed shell, on the top of described closed shell 1, contains motor part 2, contains compression mechanical part 3 in bottom.And then compression mechanical part 3 is submerged in and stores in the oil storage portion (not shown) of the lubricant oil of closed shell 1 inner bottom part.
Described compression mechanical part 3 possesses the 1st cylinder 5A on top, possess the 2nd cylinder 5B in bottom, between these the 1st cylinder 5A and the 2nd cylinder 5B, is situated between across middle demarcation strip 6.
At the upper surface of the 1st cylinder 5A, overlapping have a main bearing 7, and described main bearing 7 is installed in closed shell 1 inner circle wall.At the lower surface of the 2nd cylinder 5B, overlapping have supplementary bearing 8, and described supplementary bearing 8 and the 2nd cylinder 5B and middle demarcation strip 6 and the 1st cylinder 5A are together installed on main bearing 7.
The intermediate portion rotation of described running shaft 4 is supported in main bearing 7 freely, and underpart rotation is supported in supplementary bearing 8 freely.And then, run through the inside diameter ground of the 1st cylinder 5A and middle demarcation strip 6 and the 2nd cylinder 5B, the inside diameter of the 1st cylinder 5A and the 2nd cylinder 5B with roughly 180 ° phase difference and possess integratedly the 1st eccentric part and the 2nd eccentric part of same diameter.
There is a 1st cylinder 9a the 1st eccentric part side face is chimeric, have a 2nd cylinder 9b the 2nd eccentric part side face is chimeric.The 1st cylinder 9a and the 2nd cylinder 9b are accommodated as follows, that is: along with the rotation of running shaft 4, perisporium separately of the 1st cylinder 9a and a 2nd cylinder 9b part contacts along the inside diameter perisporium of the 1st cylinder 5A and the 2nd cylinder 5B on one side, Yi Bian make eccentric motion.
The inside diameter of described the 1st cylinder 5A is sealed by main bearing 7 and middle demarcation strip 6, forms the 1st 10A of cylinder chamber.The inside diameter of the 2nd cylinder 5B is sealed with supplementary bearing 8 by middle demarcation strip 6, forms the 2nd 10B of cylinder chamber.
It is mutually the same that the 1st diameter of 10A Yu 2 10B of cylinder chamber of cylinder chamber and the axial length of running shaft 4 are that height dimension is set to.The 1st cylinder 9a is housed in the 1st 10A of cylinder chamber, and the 2nd cylinder 9b is housed in the 2nd 10B of cylinder chamber.
On main bearing 7, be provided with overlappingly and be provided with separately the ejection baffler (muffler) 11 of spraying hole doubly, described ejection baffler 11 covers set ejection valve system 12a in main bearings 7.On supplementary bearing 8, substance ejection baffler 13 is installed, described ejection baffler 13 covers set ejection valve system 12b in supplementary bearing 8.On described ejection baffler 13, be not provided with spraying hole.
The ejection valve system 12a of main bearing 7 is communicated to the 1st 10A of cylinder chamber, open while rising to authorized pressure following compression in the 10A of cylinder chamber, and compressed gas refrigerant is ejected in ejection baffler 11.The ejection valve system 12b of supplementary bearing 8 is communicated to the 2nd 10B of cylinder chamber, open while rising to authorized pressure following compression in the 10B of cylinder chamber, and compressed gas refrigerant is ejected to ejection baffler 13.
Spread all over supplementary bearing 8, the 2nd cylinder 5B, middle demarcation strip 6 and the 1st cylinder 5A and main bearing 7 and be provided with ejection gas path of navigation.Described ejection gas path of navigation guides to Jing 2 10B of cylinder chamber compressions the gas refrigerant that is ejected to lower side ejection baffler 13 via ejection valve system 12b in the dual ejection baffler 11 of upper side.
On the other hand, in the 1st cylinder 5A, be provided with the 1st blade 15A, in the 2nd cylinder 5B, be provided with the 2nd blade 15B.Each self-contained two of being split into upper side and lower side along axially i.e. the 1st cylinder 5A of running shaft 4 and the short transverse of the 2nd cylinder 5B of the 1st blade 15A and the 2nd blade 15B are cut apart blade a, b.
As described later, an end elasticity of 1 helical spring (resilient member) 16 is connected to two rearward end of cutting apart blade a, b that form respectively the 1st blade 15A and the 2nd blade 15B.Therefore, helical spring 16 is connected to the mode of cylinder 9a, 9b to cut apart the front end of blade a, b, and cylinder 9a, 9b direction are energized.
Fig. 2 is the planimetric map of the 1st cylinder 5A, and the 2nd not shown cylinder 5B is also same plane structure.Therefore, dispense the prefix of " the 1st ", " the 2nd " and symbol " A ", " B " describes (following so same).
In cylinder 5, being provided with continuously to inside diameter is the blade groove 17 that cylinder chamber 10 opens, and then, in the rearward end of blade groove 17, be provided with continuously blade back chamber 18.In blade groove 17, to-and-fro motion contains blade 15 freely, and described blade 15 is to be in the short transverse of cylinder 5 to be divided into upper and lower two states of cutting apart blade a, b.Upper side is cut apart blade a and lower side, and to cut apart the front end of blade b interior capable of expansion and contraction in cylinder chamber 10, and rearward end is interior capable of expansion and contraction in blade back chamber 18.
The front end of cutting apart blade a, b forms roughly circular-arc when overlooking, and extend out under the state of cylinder chamber 10 in opposite directions at front end, and when overlooking, regardless of its angle of swing, described front end all forms lines with circular cylinder 9 perisporiums and contacts.
And then 1 spring accepting hole 19 is the substantial middle portion of wall thickness (axle) direction of cylinder 10 from the periphery wall of cylinder 10, via blade back chamber 18 till being set to the front that inside diameter is cylinder chamber 10.
In spring accepting hole 19, contain helical spring 16, be assembled under the state of compression mechanical part 3, an end of helical spring 16 is connected to closed shell 1 inner circle wall.The other end with the upper side that forms blade 15 cut apart blade a and lower side cut apart the mode of the equal butt of blade b and be situated between every, to respectively cutting apart blade a, b, press and energize simultaneously.
Again as shown in Figure 1, in the upper end portion of closed shell, be connected with the refrigerant pipe P of ejection use.Described refrigerant pipe P arranges to be communicated with successively the mode of condenser 20, expansion gear 21, vaporizer 22 and liquid-storage container (accumulator) 23.
And, from liquid-storage container 23 via 2 inhalant refrigerant pipe P, P and be connected in the 1st cylinder 5A and the 2nd cylinder 5B via the closed shell 1 rotary compressor K.Like this, form the freeze cycle loop R of freezing cycle device.
Again as shown in Figure 2, from the periphery wall of closed shell 1 and cylinder 5, spread all over cylinder chamber 10 and be provided with and suck with hole 25, from the inhalant refrigerant pipe P of liquid-storage container 23 branches, be inserted into and be fixed on described suction with hole 25.Clip blade 15 and blade groove 17 and in circumferencial direction one side of cylinder 5, be provided with and suck with hole 25, at opposite side, be provided with the spraying hole 26 that is communicated in described ejection valve system 12.
Follow the eccentric motion of each cylinder 9, gas refrigerant is sucked into the suction side of the cylinder chamber 10 being divided by blade 15 from inhalant refrigerant pipe P.And then the compressed side of the cylinder chamber 10 that gas refrigerant forms to division moves and is compressed.When the volume of compressed side diminishes and the pressure rise of gas refrigerant during to authorized pressure, gas refrigerant is ejected to ejection valve system 12 from spraying hole 26.
In the dual ejection baffler 11 of upper side, the gas refrigerant of the gas refrigerant of Cong 1 10A of cylinder chamber ejection and Cong 2 10B of cylinder chamber ejections confluxes, and then is discarded in closed shell 1.And, via the part that forms motor part 2 set gas path of navigation and be full of closed shell 1 upper end portion to each other, and with refrigerant pipe P, be ejected to compressor K outside from ejection.
The gas refrigerant of high pressure is conducted to condenser 20 and condensation becomes liquid refrigerant.Described liquid refrigerant is conducted to expansion gear 21 and heat insulation expansion, and is conducted to vaporizer 22 and evaporates, thereby becomes gas refrigerant.In vaporizer 22, from ambient air, capture latent heat of vaporization, play refrigeration.
If rotary compressor K is equipped in air conditioner, play the effect of thermantidote.And then the ejection side of compressor K that also can be in freeze cycle arranges four-way switching valve to form heat pump (heat pump) formula freeze cycle loop.If adopt to switch four-way switching valve, refrigeration agent mobile switched to oppositely, by directly the lead structure of indoor heat converter of the gas refrigerant from compressor K ejection, play the effect of heating installation.
, the mounting structure of blade 15 and 1 helical spring 16 is described in detail, described blade 15 comprises along upper and lower overlapping two of the short transverse of cylinder 5 and cuts apart blade a, b herein, and described 1 helical spring 16 is cut apart blade a, b to these and energized.
As shown in Figure 3, helical spring 16 is wound and is processed into, and in the contact segment with cutting apart blade a, b, forms and comprises the 16a of the portion of connecting airtight that connects airtight circle portion.Comparatively it is desirable to, the 16a of the portion of connecting airtight of helical spring 16 is more than or equal to two circles (two circles).But, also can be less than two circles.
On the other hand, on blade a, b, be provided with helical spring mounting groove 30 respectively cutting apart.Helical spring mounting groove 30 comprises: the 30a of taper portion, from cutting apart blade a, b end edge towards the setting of front end direction; And parallel portion 30b, from the described taper 30a of portion further forward end direction arrange continuously, and parallel with the vibration-direction of cutting apart blade a, b.
The 30a of taper portion cut apart blade a, b opening end is the width dimensions larger than the wire diameter of helical spring 16, the terminal (the processing end of parallel portion 30b) of the 30a of taper portion forms the width dimensions roughly the same with the wire diameter of helical spring 16.The lengthwise dimension of parallel portion 30b is less than the length of the 16a of the portion of connecting airtight in helical spring 16.
The 16a of the portion of connecting airtight of helical spring 16 embeds the parallel portion 30b of respectively cutting apart the upper set helical spring mounting groove 30 of blade a, b, so cuts apart the posture all-the-time stable of blade a, b, can prevent that it from toppling over.
Especially, if the portion 16a of connecting airtight is more than or equal to two circles, the effect of firm position after dismount and overturning-preventing is large.And, even if helical spring 16 exists the movement that departs from helical spring mounting groove 30, but owing to being provided with the 30a of taper portion, therefore easily return to reset condition.
Even if there is the impact of element precision or excessive gas load and running shaft 4 deforms, cut apart blade a, b front-end edge is connected to cylinder 9 periphery walls unevenly, but height (axial length) the size H of cutting apart blade due to every a slice becomes 1/2 when blade 15 is divided into two, therefore local reality (truly) the surface pressure Pt that touches part becomes 1/2.
On the other hand, by limiting the shape of helical spring mounting groove 30, thereby even if blade 15 departs from cylinder 9 two cut apart blade a, b and temporarily towards glide direction, depart from (for example, while producing liquid compression), helical spring 16 can not topple over or depart from yet.As long as from described recovering state to common operating condition, just can again return to normal installment state.
Like this, can reduce the real surface pressure that part is touched in part, therefore can prevent sintering or the abnormal wear of described part, can obtain the rotary compressor K of high reliability.Need no longer separately the lubricated material of special slip or surface treatment, can realize the reduction of cost.
Owing to respectively cutting apart blade a, b, slide with cylinder 9 periphery walls independently, even if therefore element precision is not too high, also can follow well cylinder 9.The gap smaller of cutting apart front-end edge and cylinder 9 periphery walls of blade a, b, the leakage of compressed gas refrigerant becomes seldom and compression performance raising.
Described in when adopting following structure, effect is particularly showing, and on main bearing 7 and supplementary bearing 8, annular (ring) groove is set, and the bending of running shaft 4 becomes large in order to relax the extreme pressure of bearing that is:.
For example, if unanimously adopt two helical springs in cutting apart the sheet number of blade a, b, must dwindle each helical spring average diameter, it is large that the restriction in design becomes., helical spring 16 is made as to one herein, therefore without the restriction in design.
If further limit helical spring 16 described above and cut apart blade a, b structure, as long as set to meet the mode of following numerical expression (1).
As shown in Fig. 4 (A), when formation being cut apart to the length dimension of the parallel portion 30b of the upper set helical spring mounting groove 30 of blade a, b and is made as the length dimension of the 16a of the portion of connecting airtight of D, helical spring 16 and be made as T,
D＜T……(1)
In addition, the width dimensions Sa of the parallel portion 30b of helical spring mounting groove 30 is roughly the same with the wire diameter S of helical spring 16.
By above restriction, even if the front-end edge of cutting apart blade a, b is connected to the periphery wall of cylinder 9 unevenly, but height (axial length) the size H of cutting apart blade due to every a slice becomes 1/2, therefore local reality (truly) the surface pressure Pt that touches part becomes 1/2.
By limiting the shape of helical spring mounting groove 30, even if blade 15 departs from cylinder 9, to cut apart blade a, b and temporarily towards glide direction, depart from for two, helical spring 16 can not topple over or depart from yet.As long as from described recovering state to common operating condition, just can again return to normal installment state.
The working part of helical spring 16 can not gone to the inner side of the parallel portion 30b of mounting groove 30, so working part can not contact (slipping) with the parallel portion 30b of mounting groove 30, can prevent losing of helical spring 16 etc.
Fig. 5 (A), Fig. 5 (B)～Fig. 7 represent the different variation of present embodiment.
Fig. 5 (A) is the front view of blade 40, and Fig. 5 (B) is the side view that the blade 40 of helical spring 50 is installed.
Forming the cutting apart on blade a, b of blade 40, be respectively equipped with the 60a of taper portion that comprises distortion and the spring fitting groove 60 of parallel portion 60b, helical spring 50 is embedded into described spring fitting groove 60.
With shape length direction quadrature, that cut apart the width direction of blade a, b that forms the parallel portion 60b of helical spring mounting groove 60, be to be the circular-arc mode equating with internal diameter and the external diameter of helical spring 50 and to form.
That is, with helical spring 50 when the side-looking rounded situation as one man, the 60a of taper portion and parallel portion 60b all form circular-arc when side-looking.Helical spring 50 is being embedded under the state of parallel portion 60b via the 60a of taper portion, and the internal-and external diameter of parallel portion 60b is unanimously in the internal-and external diameter of helical spring 50.
Therefore, can helical spring 50 be embedded to parallel portion 60b via the 60a of taper portion with smooth operation.In fact, on blade 40, during processed springs mounting groove 60, while be to make machining tool or cut apart blade a, b to rotate and process, therefore can obtain the raising of work efficiency under assembled state.
In addition, herein, what equate with the internal diameter of helical spring 50 and external diameter is circular-arc, comprises following situation: forming the parallel portion 60b of mounting groove 60 and the gap that 50 formation of helical spring can prevent the degree that helical spring 50 is significantly toppled over.
Fig. 6 (A) is the front view of blade 70, and Fig. 6 (B) is the side view that the blade 70 of helical spring 80 is installed.
Linearly with the shape of width direction length direction quadrature, that cut apart blade a, b of parallel portion 90b that forms helical spring mounting groove 90, and be the width dimensions contacting with external diameter with the internal diameter of helical spring 80.
; under the state of parallel portion 90b that helical spring 80 is embedded to spring fitting groove 90; the bight, inner side of the parallel portion 90b of blade a, b is respectively cut apart in the internal diameter contact of helical spring 80, and the outside central part of the parallel portion 90b of blade a, b is respectively cut apart in the external diameter contact of helical spring 80.As a result, the internal diameter of helical spring 80 contacts with the two parallel portion 90b of place, 90b with external diameter two positions, place at position everywhere.
If this kind of structure, can prevent helical spring 80 with respect to the off normal of the parallel portion 90b of helical spring mounting groove 90 and depart from, obtain the raising of reliability, and multi-disc blade 70 can be arranged and time processing, thereby can realize the raising of work efficiency.
In addition, now, with the width dimensions that the internal diameter of helical spring 80 contacts with external diameter, be also included within the parallel portion 90b of mounting groove 90 and the gap that 80 formation of helical spring can prevent the degree that helical spring 50 is significantly toppled over.
Fig. 7 only represents the compression mechanical part 3 of the rotary compressor Ka of variation.
Constant, be still the rotary compressor Ka of two cylinder type, on the other hand, constant, be for example arranged on blade 15A in the 1st cylinder 5A and comprise two and cut apart blade a, b, and utilize a helical spring 16 to energize.
Constant, be arranged on blade 15B in the 2nd cylinder 5B and also comprise two and cut apart blade a, b, but do not have helical spring herein.The substitute is, expose to closed shell 1 blade back chamber 18, to be subject to the impact of closed shell 1 internal pressure.
Running shaft 4 is rotarilyd actuate, and in 1 10A of cylinder chamber, along with the eccentric motion of cylinder 9a, the 1st blade 15A is energized by helical spring 16 and be reciprocating.In the 2nd 10B of cylinder chamber, cylinder 9b makes eccentric motion, but due in closed shell 1 still for low pressure is not subject to back pressure, therefore the 2nd blade 15B is pushed aside by cylinder 9b and guarantees going-back position.
In Jin 1 10A of cylinder chamber, carry out compression, the gas refrigerant of compressed high pressure is discarded in closed shell 1.Therefore, the pressure in closed shell 1 rises gradually, when gassy refrigeration agent, from the refrigerant pipe P of ejection use, is ejected to freeze cycle loop.The variation of the gas refrigerant that is directed to freeze cycle loop as presenting as previously explained, thus carry out refrigeration.
On the other hand, the gas refrigerant of emitting by Cong 1 10A of cylinder chamber, the pressure rise in closed shell 1, to the high pressure of regulation, exposes to the blade back chamber 18 in closed shell 1 also gassy refrigeration agent.Therefore, the 2nd blade 15B is pressed into cylinder 9b as back pressure by front end using the gas refrigerant that is full of the high pressure of blade back chamber 18, reciprocating to follow cylinder 9b.
Like this, in 1 10A of cylinder chamber, along with running starts just to carry out compression, on the other hand, in 2 10B of cylinder chamber, be in closed shell 1, to be full of under the state of compressed gas refrigerant just to start compression.
Although Yu 1 10A of cylinder chamber separates the compression that the time difference starts the 2nd 10B of cylinder chamber, than the few helical spring of the rotary compressor K of previously described present embodiment, correspondingly, spring accepting hole need not be set, therefore contribute to cost.
Above, present embodiment is illustrated, but above-mentioned mode of execution is only illustration, is not intended to limit the scope of mode of execution.Described mode of execution can be implemented with other variety of way, within not departing from the scope of purport, can carry out various omissions, replacement, change.These mode of executions or its distortion are included in the scope or purport of model utility, and in the scope impartial with it.
Claims (6)
1. a rotary compressor, the compression mechanical part of accommodating motor part and linking with described motor part via running shaft in closed shell, described rotary compressor is characterised in that, described compression mechanical part comprises:
Cylinder, has cylinder chamber;
Cylinder is made eccentric motion in described cylinder chamber;
Blade, is connected to described cylinder and moves back and forth, and will in described cylinder chamber, be divided into compressed side and suction side; And
Helical spring, is connected to the rear end side of described blade, and the mode that is connected to described cylinder with described blade front end is energized towards cylinder direction to described blade,
Described blade be described running shaft be axially in the short transverse of described cylinder, overlapping configuration has two to cut apart blade,
Described helical spring is cut apart the mode of blade and form to press described two with a helical spring, and is possessing with the described contact segment of cutting apart blade the portion of connecting airtight,
The described blade of cutting apart possesses the helical spring mounting groove that comprises taper portion and parallel portion, described taper portion is from cutting apart blade end edge towards the setting of front end direction, described parallel portion be from described taper portion further forward end direction arrange continuously, and parallel with the vibration-direction of described blade.
2. rotary compressor according to claim 1, is characterized in that,
When the length dimension of cutting apart the parallel portion of the helical spring mounting groove on blade described in being located at being made as to D, the described helical spring length dimension that connects airtight portion and being made as T, to meet the mode of following numerical expression, set: D < T.
3. rotary compressor according to claim 1, is characterized in that,
With form described helical spring mounting groove described parallel portion length direction quadrature, described in cut apart the shape of the width direction of blade, be equate with described helical spring internal diameter and external diameter circular-arc.
4. rotary compressor according to claim 1, is characterized in that,
With form described helical spring mounting groove described parallel portion length direction quadrature, described in to cut apart the shape of width direction of blade linearly, and be the width dimensions contacting with external diameter with described helical spring internal diameter.
5. a rotary compressor, is characterized in that,
In the described rotary compressor of described claim 1 with a plurality of cylinders, to described, cut apart the described helical spring that blade energizes and be only arranged in 1 cylinder in described a plurality of cylinder, described in possessing for cylinder described in other, cut apart blade, replace helical spring and external pressure in described closed shell as back pressure.
6. a freezing cycle device, is characterized in that,
Described freezing cycle device forms freeze cycle loop, and described freeze cycle loop is that arbitrary described rotary compressor and condenser, expansion gear in claim 1 to 5 are communicated with via refrigerant pipe with vaporizer.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-177222 | 2012-08-09 | ||
| JP2012177222A JP2014034940A (en) | 2012-08-09 | 2012-08-09 | Rotary compressor and refrigeration cycle device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203463285U true CN203463285U (en) | 2014-03-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320481580.1U Expired - Lifetime CN203463285U (en) | 2012-08-09 | 2013-08-07 | Rotary compressor and refrigeration cycle device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2014034940A (en) |
| CN (1) | CN203463285U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106401960A (en) * | 2015-07-28 | 2017-02-15 | 东芝开利株式会社 | Rotary compressor and refrigeration cycle device |
| CN107288884A (en) * | 2017-07-18 | 2017-10-24 | 宁波奇尘电子科技有限公司 | A kind of rotary type cold device |
| CN107709785A (en) * | 2015-09-28 | 2018-02-16 | 东芝开利株式会社 | Rotary compressor and freezing cycle device |
| CN111720311A (en) * | 2020-06-18 | 2020-09-29 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigeration cycle system |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104884807B (en) * | 2013-03-27 | 2016-11-09 | 东芝开利株式会社 | Rotary compressor and refrigerating circulatory device |
| CN106401918A (en) * | 2016-10-17 | 2017-02-15 | 珠海凌达压缩机有限公司 | Air cylinder and compressor |
| JP7190605B1 (en) | 2022-06-24 | 2022-12-15 | 日立ジョンソンコントロールズ空調株式会社 | Rotary compressor and air conditioner |
-
2012
- 2012-08-09 JP JP2012177222A patent/JP2014034940A/en active Pending
-
2013
- 2013-08-07 CN CN201320481580.1U patent/CN203463285U/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106401960A (en) * | 2015-07-28 | 2017-02-15 | 东芝开利株式会社 | Rotary compressor and refrigeration cycle device |
| CN106401960B (en) * | 2015-07-28 | 2019-11-12 | 东芝开利株式会社 | Rotary compressor and freezing cycle device |
| CN107709785A (en) * | 2015-09-28 | 2018-02-16 | 东芝开利株式会社 | Rotary compressor and freezing cycle device |
| US10294940B2 (en) | 2015-09-28 | 2019-05-21 | Toshiba Carrier Corporation | Rotary compressor and refrigerating cycle device |
| CN107288884A (en) * | 2017-07-18 | 2017-10-24 | 宁波奇尘电子科技有限公司 | A kind of rotary type cold device |
| CN111720311A (en) * | 2020-06-18 | 2020-09-29 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigeration cycle system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2014034940A (en) | 2014-02-24 |
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Granted publication date: 20140305 |