CN203796562U - Rotating piston type compressor - Google Patents
Rotating piston type compressor Download PDFInfo
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- CN203796562U CN203796562U CN201420172422.2U CN201420172422U CN203796562U CN 203796562 U CN203796562 U CN 203796562U CN 201420172422 U CN201420172422 U CN 201420172422U CN 203796562 U CN203796562 U CN 203796562U
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- 238000003825 pressing Methods 0.000 claims abstract description 60
- 230000033001 locomotion Effects 0.000 claims abstract description 11
- 238000005057 refrigeration Methods 0.000 claims description 32
- 230000006835 compression Effects 0.000 claims description 31
- 238000007906 compression Methods 0.000 claims description 31
- 239000002184 metal Substances 0.000 claims description 7
- 238000004381 surface treatment Methods 0.000 claims description 4
- 238000000926 separation method Methods 0.000 claims description 3
- 238000003754 machining Methods 0.000 abstract description 5
- 239000003795 chemical substances by application Substances 0.000 description 29
- 239000003507 refrigerant Substances 0.000 description 5
- 238000006243 chemical reaction Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000003584 silencer Effects 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000007086 side reaction Methods 0.000 description 2
- FGRBYDKOBBBPOI-UHFFFAOYSA-N 10,10-dioxo-2-[4-(N-phenylanilino)phenyl]thioxanthen-9-one Chemical compound O=C1c2ccccc2S(=O)(=O)c2ccc(cc12)-c1ccc(cc1)N(c1ccccc1)c1ccccc1 FGRBYDKOBBBPOI-UHFFFAOYSA-N 0.000 description 1
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 1
- 235000011089 carbon dioxide Nutrition 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 239000008400 supply water Substances 0.000 description 1
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- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The utility model relates to a rotating piston type compressor. Even if high-precision machining is not carried out on a vane groove, a vane can follow a piston. The rotating piston type compressor is provided with a compressing mechanism part which comprises a cylinder body, the piston and the vane. A cylinder-shaped cylinder body chamber is formed. The piston is arranged on an eccentric part of a shaft in a free-sliding mode. The piston and the eccentric part carry out eccentric rotating motion in the cylinder body chamber. The vane is arranged at the vane groove formed in the cylinder body in a free-sliding mode. Through pressing force exerted at one end of the vane, the other end of the vane is in abutting connection with the outer periphery face of the piston. The inner portion of the cylinder chamber is divided into a sucking-in chamber and a compressing chamber. In a section, perpendicular to a center shaft, of the cylinder chamber, the end of one side, in abutting connection with the piston, of the vane forms an arc shape, and the center of the arc shape deviates to the side of the compressing chamber in the center line in the length direction relative to the vane.
Description
Technical field
The utility model has related to such as the utilization of refrigeration and cold storage idle call equipment and heat supply water equipment etc. the rotary-piston type compressor using in the freeze cycle of heat pump.
Background technique
The compression mechanical part of rotary-piston type compressor in the past possesses: cylinder body, and it forms cylinder body cylindraceous chamber; Piston, it is installed on the eccentric part of the axle being rotated by motoring in the mode being free to slide, move together with this eccentric part at the indoor eccentric rotary of cylinder body; And blade, it is arranged at the blade groove that is formed on cylinder body in the mode being free to slide, the pressing force that an end is given in utilization makes the outer circumferential face butt of another end and piston, by above-mentioned cylinder body indoor separation, is suction chamber and pressing chamber (with reference to patent documentation 1).
And, at the section vertical with central shaft of cylinder body chamber (for example, in the situation that the perpendicular type rotary-piston type compressor of putting that is set up in parallel along the vertical direction motor and compression mechanical part is for cross section) the middle compression mechanical part of observing such rotary-piston type compressor in the past, the end of blade and side piston butt (following, to be called " front end ") forms circular shape.In addition, with the central shaft vertical section Leaf of the center of this circular shape in cylinder body chamber is on the center line (by the center of width of blade, extending the virtual line of configuration along length of blade direction) of length direction.
Patent documentation 1: Japanese kokai publication sho 58-220993 communique (the 2nd, 3 figure etc.)
Fig. 5 means near the enlarged view of blade of rotary-piston type compressor in the past.In addition, Fig. 6 is in the explanatory drawing of the blade of rotary-piston type compressor in the past power relation around for illustration.In addition, Fig. 5 and Fig. 6 mean the figure of the section vertical with central shaft of cylinder body chamber.
Rotary-piston type compressor in the past become blade 11 not with end (in the situation that radially the observing and becoming outboard end from cylinder body chamber of a side of piston 9 butts.Below, be called " back side end ") the position configuration in outside have spring.And, by the reaction force of this spring, to vacuum side of blade side end, give pressing force.In addition, refrigeration agent after the compression of portion of compressed mechanism is discharged in the rotary-piston type compressor of the high pressure shell-type in closed container, take in the hole portion of above-mentioned spring with in situation about being connected in closed container, the refrigerant pressure in closed container (pressure of the refrigeration agent after portion of compressed mechanism compression) also as pressing force be endowed blade not with the end of a side of piston butt.Therefore the pressure P d, being brought by the reaction force (pressure that according to circumstances, comprises the refrigeration agent in closed container) of spring in the back side end effect of blade 11.In addition, with the contacting part 201(between the front end of blade 11 and the outer circumferential face of piston 9 in the plane vertical with central shaft of cylinder body chamber, the position that the central point of circular shape of the front end of connection blade 11 and the straight line of the central point of piston 9 and the front end of blade 11 are crossing) be boundary, to this front end from suction chamber 12 actuating pressure Ps, from pressing chamber 13 side actuating pressure Pc.Therefore, as shown in Figure 5, by the blade front end pushing force Fv producing because acting on pressure (Pd) and the pressure difference that acts on the pressure (Ps, Pc) of front end of the back side end of blade 11, the outer circumferential face of the front end of blade 11 and piston 9 connects.
In addition, in rotary-piston type compressor in the past during compressed refrigerant, to the power shown in the indoor outstanding partial action Fig. 6 of the cylinder body to cylinder body 5 in blade 11.Specifically, between blade 11 and blade groove 10, there is the gap 21 of several microns.In addition, when compressed refrigerant, the pressure load P that blade 11 produces by the differential pressure because of pressing chamber 13 and suction chamber 12 this gap 21 that tilts minutely.Therefore, blade 11 is that contacting part 301 contacts in the suction side of blade groove 10 and the end of suction chamber 12 sides, in the discharge side of blade groove 10 and the end of pressing chamber 13 sides, is that contacting part 302 contacts.In other words, at these contacting parts, produce respectively suction side reaction force N1 and discharge side reaction force N2.If the friction factor of contacting part 301 is defined as to μ 1, the friction factor of contacting part 302 is defined as to μ 2, the frictional force f1 that blade 11 produces in suction side when the interior slip of blade groove 10 is μ 1 * N1, the frictional force f2 producing in discharge side is μ 2 * N2.Therefore,, below the summation Fside(of the frictional force producing in the side face of blade 11, be called " blade side frictional force ") by Fside=f1+f2=μ 1 * N1+ μ 2 * N2, represented.
Fig. 7 means that in rotary-piston type compressor in the past piston is at the figure of the relation of pressure that cylinder body is indoor while carrying out eccentric rotary motion, in pressing chamber and blade side frictional force.In addition, Fig. 8 means that in this rotary-piston type compressor piston is at the figure of the relation of pressure that cylinder body is indoor while carrying out eccentric rotary motion, in pressing chamber and blade front end pushing force.
Herein, in Fig. 7, transverse axis represents to make the phase place ［ deg ］ (angle of swing) of the axle of piston 9 eccentric rotaries motions, and the longitudinal axis in left side represents the pressure P c ［ MPa ］ in pressing chamber 13, and the longitudinal axis on right side represents blade side frictional force Fside ［ N ］.In addition, in Fig. 8, transverse axis represents to make the phase place ［ deg ］ (angle of swing) of the axle of piston 9 eccentric rotaries motions, and the longitudinal axis in left side represents the pressure P c ［ MPa ］ in pressing chamber 13, and the longitudinal axis on right side represents blade front end pushing force Fv ［ N ］.
In addition,, in Fig. 7 and Fig. 8, the phase place 0 ［ deg ］ of axle represents the state that piston 9 and blade groove 10 are nearest.In addition, the phase place 0 ［ deg ］ of axle represents piston 9 and blade groove 10 state farthest.
As shown in Figure 7, along with the phase advance of axle (in other words, piston 9), the volume in pressing chamber 13 reduces, and the pressure P c in pressing chamber 13 rises.And if the pressure P c in pressing chamber 13 reaches authorized pressure (=head pressure), the refrigeration agent in pressing chamber 13 is discharged by illustrated exhaust port never, the pressure in pressing chamber 13 afterwards becomes constant.Now, blade side frictional force Fside is also identical with the pressure P c in pressing chamber 13, till being increased to pressure P c in pressing chamber 13 and reaching authorized pressure (=head pressure), under this authorized pressure (=head pressure), becomes maximum value.This is because along with pressure P c in pressing chamber 13 rises, and the pressure load P producing because of the differential pressure of pressing chamber 13 and suction chamber 12 increases gradually.On the other hand, as shown in Figure 8, till blade front end pushing force Fv is reduced to pressure P c in pressing chamber 13 and reaches authorized pressure (=head pressure), and become minimum value under this authorized pressure (=head pressure).
Herein, the phase place of axle (in other words piston 9) from 0 ［ deg ］ to 180 ［ deg ］ during, piston 9 departs from from blade groove 10.Therefore, blade 11 is in order to follow the action of such piston 9, Yi Bian need by blade front end pushing force Fv, blade 11 to be moved it to piston 9 pushings on one side.In other words, need to make blade front end pushing force Fv > blade side frictional force Fside.In addition, the phase place of axle (in other words piston 9) is below 180 ［ deg ］, and piston 9 approaches with blade groove 10.Therefore, blade 11 is pressed into blade groove 10 by piston 9, so it doesn't matter for blade front end pushing force Fv and blade side frictional force Fside, can follow the action of piston 9.
Yet, using CO
2in the situation of the low compression ratio running rotary-piston type compressor during in the situation of the refrigeration agent that the such polytropic index of refrigeration agent (carbonic acid gas refrigeration agent) is high and with underload, it is front that the phase place of axle (in other words piston 9) reaches 180 ［ deg ］, and the pressure P c in pressing chamber 13 easily reaches authorized pressure (=head pressure).In other words, using CO
2in the situation of the low compression ratio running rotary-piston type compressor during in the situation of the refrigeration agent that the such polytropic index of refrigeration agent is higher and with underload, blade 11 need to make under the state of blade front end pushing force Fv > blade side frictional force Fside in order to follow the action of piston 9, and the pressure P c in pressing chamber 13 reaches authorized pressure (=head pressure).Therefore, for rotary-piston type compressor in the past, if the pressure P c in pressing chamber 13 reaches blade front end pushing force Fv < blade side frictional force Fside till authorized pressure (=head pressure), blade 11 just cannot enough be followed the action of piston 9.
Fig. 9 and Figure 10 are for illustrating that blade follows the explanatory drawing of the problem producing in the situation of piston.In addition the phase place that, Fig. 9 illustrates axle (in other words piston) position relationship during from 0 ［ deg ］ to 180 ［ deg ］, blade and piston.In addition, Figure 10 illustrates the indoor flow of refrigerant of cylinder body under the state of Fig. 9 (c).
Shown in Fig. 9 (a), the phase place of axle (in other words piston 9) starts the compression step of refrigeration agent while becoming 0 ［ deg ］.Afterwards, in this compression step, to (with reference to Fig. 9 (b)) under the state of blade front end pushing force Fv > blade side frictional force Fside, blade 11 can be followed the action of piston 9.Yet refrigeration agent pressure P c compressed and in pressing chamber 13 approaches authorized pressure (=head pressure), and blade front end pushing force Fv reduction, blade side frictional force Fside increases.Therefore, as shown in Figure 9 (c), if blade front end pushing force Fv lower than blade side frictional force Fside, blade 11 cannot be followed piston 9 and be departed from.If blade 11 departs from from piston 9, the pressure difference that refrigeration agent flows into suction chamber Room 12, two from pressing chamber 13 is dwindled, and the pressure P c in pressing chamber 13 reduces, so as shown in Fig. 9 (d), it is large that blade front end pushing force Fv becomes.Therefore, on one side exist blade 11 again towards piston 9 one side speedups, move and collide and contact again with piston 9, so contacting part sustains damage or produces the such problem points of impact sound.
In addition, as shown in figure 10, if blade 11 departs from piston 9, as shown in arrow 22, the higher pressure refrigerant gas of pressing chamber 13 is revealed to suction chamber 12 sides, and the performance that also produces thus rotary-piston type compressor reduces such problem points.
In addition, in rolling piston compressor in the past in order to solve the above problems a little, thereby also considered that the blade groove 10 of cylinder body 5 is implemented to high-precision abrasive machining reduced the coefficientoffrictionμ 1 while sliding, the technology of μ 2.Yet high-precision abrasive machining processing cost rises, rotary-piston type compressor becomes at high price if the blade groove 10 of cylinder body 5 is implemented.
Model utility content
The utility model completes in order to solve problem points as described above, even if its object is to provide a kind of, blade groove is not implemented to the rotary-piston type compressor that high-precision machining blade also can be followed piston.
The related rotary-piston type compressor of the utility model possesses: motor, and this motor has stator and rotor; Axle, one end of this axle is fixed in described rotor, and is formed with eccentric part; Compression mechanical part, this compression mechanical part has: the cylinder body that forms cylinder body cylindraceous chamber; Piston, it is installed on described eccentric part in the mode being free to slide and carries out eccentric rotary motion described cylinder body is indoor together with this eccentric part; And blade, it is arranged at the blade groove that is formed on described cylinder body in the mode being free to slide, utilize the pressing force give an end to make the outer circumferential face butt of another end and described piston, by described cylinder body indoor separation, is suction chamber and pressing chamber; And closed container, this closed container is taken in described motor, described axle and described compression mechanical part, in the section vertical with central shaft of described cylinder body chamber, described blade form circular shape with the end of a side described piston butt, with respect to described blade, the center line at length direction moves to pressing chamber lateral deviation at the center of this circular shape.
Preferably in the related rotary-piston type compressor of the utility model, in the section vertical with central shaft of described cylinder body chamber, at the center line of length direction, the center line with respect to the described cylinder body chamber parallel with this center line moves to described suction chamber lateral deviation described blade groove.
Preferably, in the related rotary-piston type compressor of the utility model, the surface of described blade has been implemented surface treatment, makes the surface of described blade and the mother metal of this blade compare wearability and improves.
Preferably, in the related rotary-piston type compressor of the utility model, the refrigeration agent of use is CO
2refrigeration agent.
The related rotary-piston type compressor of the utility model is in the section vertical with central shaft of cylinder body chamber, blade form circular shape with the end of side piston butt, with respect to blade, the center line at length direction moves to pressing chamber lateral deviation at the center of this circular shape.Therefore, the related rotary-piston type compressor of the utility model is compared with rotary-piston type compressor in the past, in the end of blade and side piston butt, increases, and reduce from the pressure P c of pressing chamber effect from the pressure P s of suction chamber effect.Therefore, the related rotary-piston type compressor of the utility model is compared with rotary-piston type compressor in the past, can increase because acting on the blade front end pushing force Fv not producing with the pressure of the end of a side of piston butt and the pressure difference acting on the pressure of the end of a side of piston butt of blade.
, the related rotary-piston type compressor of the utility model is by increasing blade front end pushing force Fv, even if the blade groove of cylinder body is not implemented to high-precision abrasive machining, using CO
2in the situation of the low compression ratio running rotary-piston type compressor during in the situation of the refrigeration agent that the such polytropic index of refrigeration agent is higher and with underload, also can make blade follow piston.
Accompanying drawing explanation
Fig. 1 means the longitudinal section of the rotary-piston type compressor that mode of execution 1 of the present utility model is related.
Fig. 2 means the sectional elevation of the compression mechanical part of the rotary-piston type compressor that mode of execution 1 of the present utility model is related.
Fig. 3 means near the enlarged view of blade of the rotary-piston type compressor that mode of execution 1 of the present utility model is related.
Fig. 4 means the figure of the cylinder body of the rotary-piston type compressor that mode of execution 2 of the present utility model is related, means near the enlarged view that blade groove is.
Fig. 5 means near the enlarged view of blade of rotary-piston type compressor in the past.
Fig. 6 is in the explanatory drawing of the blade of rotary-piston type compressor in the past power relation around for illustration.
Fig. 7 means that in rotary-piston type compressor in the past piston is at the figure of the relation of pressure that cylinder body is indoor while carrying out eccentric rotary motion, in pressing chamber and blade side frictional force.
Fig. 8 means that in rotary-piston type compressor in the past piston is at the figure of the relation of pressure that cylinder body is indoor while carrying out eccentric rotary motion, in pressing chamber and blade front end pushing force.
Fig. 9 is for the explanatory drawing of the problem producing when blade cannot be followed piston is described.
Figure 10 is for the explanatory drawing of the problem that blade produces in the time of cannot following piston is described.
Description of reference numerals
1 ... closed container; 2 ... stator; 3 ... rotor; 4 ... axle; 4a ... main shaft; 4b ... countershaft; 4c ... eccentric part, 5 ... cylinder body; 6 ... cylinder body chamber; 6a ... center line (cylinder body chamber); 7 ... upper bearing (metal); 8 ... lower bearing; 9 ... piston; 10 ... blade groove; 10a ... center line (blade groove); 11 ... blade; 11a ... center line (blade); 11b ... center; 12 ... suction chamber; 13 ... pressing chamber; 14 ... spring; 15 ... hole portion; 17 ... suction port; 18 ... exhaust port; 19 ... exhaust silencer; 20 ... exhaust silencer chamber; 21 ... the gap of blade and blade groove; 22 ... refrigeration agent is revealed to suction chamber from pressing chamber; 100 ... rotary-piston type compressor; 101 ... compression mechanical part; 102 ... motor part; 201 ... contacting part (in the past); 202 ... contacting part (mode of execution 1); 301 ... blade and blade groove are at the contacting part of suction chamber side; 302 ... blade and blade groove are at the contacting part of discharge chamber side.
Embodiment
Below, use accompanying drawing, with reference to accompanying drawing on one side the mode of execution of the utility model related rotary-piston type compressor described on one side.In addition the mode of execution that, the utility model is not illustrated below limits.In addition, the big or small relation situation different from actual size that comprises Fig. 1 existence each component parts in the following drawings.In addition, in each following mode of execution, the identical formation of rotary-piston type compressor with is in the past marked to identical reference character.
Mode of execution 1.
Fig. 1 means the longitudinal section of the rotary-piston type compressor that mode of execution 1 of the present utility model is related.In addition, Fig. 2 means the sectional elevation of the compression mechanical part of this rotary-piston type compressor.In addition, the single stage compression rotary-piston type compressor that possesses a compression mechanical part is shown in this embodiment.
The related rotary-piston type compressor 100 of present embodiment 1 possesses closed container 1 cylindraceous, be configured in the motor part 102 of closed container 1 upper inside, be configured in motor part 102 downsides and the compression mechanical part 101 being driven by motor part 102 and the driving force of motor part 102 is passed to the axle 4 of compression mechanical part 101.
The stator 2 that motor part 102 is installed in the form of a ring by the inner peripheral surface of the upper inside along closed container 1 and in the inner side of stator 2, some gaps are set and the rotor 3 that inserts forms, rotor 3 is vertically fixed on axle 4 at central part.
Axle 4 have the rotor 3 that is fixed on motor part 102 main shaft 4a, be arranged at main shaft 4a opposition side countershaft 4b and be formed at main shaft 4a and countershaft 4b between eccentric part 4c.
Compression mechanical part 101 as shown in Figure 1 and Figure 2, possesses cylinder body 5, piston 9 and blade 11 etc.
Cylinder body 5 is fixed on the inner peripheral surface of closed container 1, and heart portion has cylinder body cylindraceous chamber 6 therein.And the mode that is provided with to be free to slide in this cylinder body chamber 6 is arranged on the piston 9 of the eccentric part 4c of axle 4.In addition, the axial both ends of the surface of the cylinder body chamber 6 of cylinder body 5 are by upper bearing (metal) 7 and lower bearing 8 sealings.These upper bearing (metal)s 7 and lower bearing 8 keep 4 main shaft 4a and countershaft 4b in the mode rotating freely.
And, in cylinder body 5, along cylinder body chamber 6, be radially formed with blade groove 10.This blade groove 10 is communicated with cylinder body chamber 6, is provided with at the interior reciprocating blade 11 of this blade groove 10 in this blade groove 10.In addition, in the situation that become blade 11 (from cylinder body chamber 6, radially do not observe the end that becomes outside with the end of a side of piston 9 butts.Below, be called " back side end ") the position configuration in outside have spring 14.And, by the reaction force of this spring 14, to the back side end of blade 11, give pressing force.In addition, the related rotary-piston type compressor 100 of present embodiment 1 be the refrigeration agent of portion of compressed mechanism 101 compression to the rotary-piston type compressor of the high pressure shell-type of closed container 1 interior discharge, the hole portion 15 of taking in spring 14 is communicated with closed container 1 is interior.Therefore, the pressure of the refrigeration agent in closed container 1 (pressure of the refrigeration agent of portion of compressed mechanism 101 compressions) is also endowed the back side end of blade 11 as pressing force.And, blade 11 (following with the end of sides piston 9 butts because acting on, be called " front end ") power and above-mentioned pressing force poor that acts on the back side end of blade 11, blade front end pushing force Fv acts on blade 11, by this blade front end pushing force Fv, the outer circumferential face butt of the front end of blade 11 and piston 9.Thus, in cylinder body chamber 6, (space more specifically, being separated by the inner peripheral surface of the outer circumferential face of piston 9 and cylinder body chamber 6) is separated into suction chamber 12 and pressing chamber 13 by blade 11.
Herein, the related rotary-piston type compressor 100 of present embodiment 1 forms the front end of blade 11 as shown in Figure 3.
Fig. 3 means near the enlarged view of blade of the rotary-piston type compressor that mode of execution 1 of the present utility model is related.This Fig. 3 is sectional elevation (figure that represents the section vertical with central shaft of cylinder body chamber 6).In addition, in Fig. 3, utilize double dot dash line that the blade of rotary-piston type compressor in the past is also shown.
As shown in Figure 3, the front end of the related blade 11 of present embodiment 1 forms circular shape.And the center 11b of this circular shape passes through the center of the width of blade 11 at the center line 11a(of length direction with respect to blade 11, extend the virtual line of configuration along the length direction of blade 11), to pressing chamber 13 lateral deviations, move (departing from) size α.In other words, for the front end of the related blade 11 of present embodiment 1, the contacting part 201 of the contacting part 202 ratios blade in the past between this front end and the outer circumferential face of piston 9 is more by pressing chamber 13 sides.In other words, the front end of the blade 11 that present embodiment 1 is related is compared with blade in the past, and it is large that the area exposing in suction chamber 12 sides becomes, and the area exposing in pressing chamber 13 sides diminishes.In addition, in present embodiment 1, blade 11 at the center line 11a of length direction with the center line (by the central shaft of cylinder body chamber 6, the straight line parallel with center line 11a) of the cylinder body chamber 6 parallel with this center line 11a in same position.
In present embodiment 1, utilize two kinds of different circular arcs of radius to form the front end of blade 11 herein.Be not limited to this, also can utilize the circular arc of a kind of radius to form the front end of blade 11, also can utilize 3 kinds of above circular arcs to form the front end of blade 11.With respect to blade 11, the center line at length direction moves to pressing chamber 13 lateral deviations at the center of the circular arc of the front end of formation blade 11.
Next, the action of the rotary-piston type compressor 100 forming is as described above described.If motor part 102 is started rotor 3 rotations, the piston 9 of eccentric part 4c that is arranged on axle 4 is at the interior eccentric motion in cylinder body chamber 6 together with having fixed the rotation of axle 4 of rotor 3, and blade 11 is in the interior to-and-fro motion of blade groove 10.Thus, the suction chamber 12 being separated by blade 11 and the volume of pressing chamber 13 change.Because of this volume-variation, from suction port 17, be drawn into the duty cryogen of suction chamber 12 compressed and become High Temperature High Pressure, from pressing chamber 13, through exhaust ports 18, the exhaust silencer chamber 20 that impaled by upper bearing (metal) 7 and exhaust silencer 19, be discharged in closed container 1.
In the compression step of refrigeration agent as described above, as shown in Figure 3, the pressure P d being brought by the reaction force of spring 14 and the pressure of the refrigeration agent in closed container 1 in the effect of the back side end of blade 11.In addition, with contacting part 202Wei circle between the front end of blade 11 and the outer circumferential face of piston 9, to this front end from suction chamber 12 actuating pressure Ps, from pressing chamber 13 side actuating pressure Pc.Therefore, as shown in Figure 3, by the blade front end pushing force Fv producing because acting on pressure (Pd) and the pressure difference that acts on the pressure (Ps, Pc) of front end of the back side end of blade 11, the outer circumferential face butt of the front end of blade 11 and piston 9.
In addition, in the compression step of refrigeration agent as described above, as shown in Figure 6, at the side face generation blade side frictional force Fside of blade 11.
Therefore, using CO
2the situation of the low compression ratio running rotary-piston type compressor during in the situation of the refrigeration agent that the such polytropic index of refrigeration agent is higher and with underload is inferior, also may be at the eccentric part 4c(of axle 4 piston 9 in other words) phase place to become 180 ［ deg ］ front, pressure P c in pressing chamber 13 reaches in the situation of authorized pressure (=head pressure), blade front end pushing force Fv is lower than blade side frictional force Fside, and blade 11 is not followed piston 9 and departed from.
Yet, in present embodiment 1, as shown in Figure 3, in cross section is looked, the center 11b of the circular shape of the front end of blade 11 with respect to blade 11 at the center line 11a of length direction to pressing chamber 13 side offset dimensions α.In other words, the front end of the blade 11 of present embodiment 1 is compared with blade in the past, and it is large that the area exposing in suction chamber 12 sides becomes, and the area exposing in pressing chamber 13 sides diminishes.Therefore, the related rotary-piston type compressor 100 of present embodiment 1 is compared with rotary-piston type compressor in the past, and the pressure P s that acts on the front end of blade 11 from suction chamber 12 increases, and the pressure P c that acts on the front end of blade 11 from pressing chamber 13 reduces.In other words, the related rotary-piston type compressor 100 of present embodiment 1 is compared with rotary-piston type compressor in the past, and blade front end pushing force Fv increases.
Therefore, at the related rotary-piston type compressor 100 of present embodiment 1, use CO
2the situation of the low compression ratio running rotary-piston type compressor during in the situation of the refrigeration agent that the such polytropic index of refrigeration agent is higher and with underload is inferior, the eccentric part 4c(of axle 4 is piston 9 in other words) phase place to become 180 ［ deg ］ front, pressure P c in pressing chamber 13 reaches in the situation of authorized pressure (=head pressure), also can prevent that blade front end pushing force Fv is lower than blade side frictional force Fside, and can prevent blade 11 from not following piston 9 and the situation (can improve the tracing ability of 11 pairs of pistons 9 of blade) of disengaging.
In addition, also can implement surface treatment to the surface of blade 11, so that wearability is compared on the surface of the related blade 11 of present embodiment 1 with the mother metal of this blade 11, improve.As described above, the related rotary-piston type compressor 100 of present embodiment 1 is compared with the past, blade front end pushing force Fv increases, but by the surface of blade 11 being implemented to improve the surface treatment of wearability, can improve the sliding mode in the surface of contact of blade 11 and piston 9.
Mode of execution 2.
Fig. 4 means the figure of the cylinder body of the rotary-piston type compressor that mode of execution 2 of the present utility model is related, means near the enlarged view that blade groove is.
In addition, Fig. 4 is sectional elevation (figure that represents the section vertical with central shaft of cylinder body chamber 6).
In mode of execution 1, blade 11 at the center line 11a(of length direction in other words, blade groove 10 is at the center line 10a of length direction) with the center line 6a(of the cylinder body chamber 6 parallel with this center line 11a by the central shaft of cylinder body chamber 6, the straight line parallel with center line 11a) in same position.
On the other hand, as shown in Figure 4,5, in present embodiment 2, at the center line 11a(of length direction in other words, blade groove 10 is at the center line 10a of length direction for blade 11) with respect to the center line 6a of the cylinder body chamber 6 parallel with this center line 11a, to suction chamber 12 lateral deviations, move size beta (departing from).
Like this, by the center line 11a of the length direction of blade 11 is moved to suction chamber 12 lateral deviations, can make the front end of the blade 11 in present embodiment 2 and the contacting part of the outer circumferential face of piston 9 compare with the front end of blade 11 and the contacting part 202 of the outer circumferential face of piston 9 in mode of execution 1, further rely on pressing chamber 13 sides.Therefore, the related rotary-piston type compressor 100 of present embodiment 2 is compared with the rotary-piston type compressor 100 shown in mode of execution 1, the pressure P s that acts on the front end of blade 11 from suction chamber 12 further increases, and the pressure P c that acts on the front end of blade 11 from pressing chamber 13 further reduces.In other words, the related rotary-piston type compressor 100 of present embodiment 2 is compared with the rotary-piston type compressor 100 shown in mode of execution 1, can further make blade front end pushing force Fv increase.
Therefore, at the related rotary-piston type compressor 100 of present embodiment 2, use CO
2the situation of the low compression ratio running rotary-piston type compressor during in the situation of the refrigeration agent that the such polytropic index of refrigeration agent is higher and with underload is inferior, the eccentric part 4c(of axle 4 is piston 9 in other words) phase place to become 180 ［ deg ］ front, pressure P c in pressing chamber 13 reaches in the situation of authorized pressure (=head pressure), also can further prevent that blade front end pushing force Fv is lower than blade side frictional force Fside, and can further prevent blade 11 from not following piston 9 and the situation (can further improve the tracing ability of 11 pairs of pistons 9 of blade) of disengaging.
Claims (4)
1. a rotary-piston type compressor, possesses:
Motor, this motor has stator and rotor;
Axle, one end of this axle is fixed in described rotor, and is formed with eccentric part;
Compression mechanical part, this compression mechanical part has: the cylinder body that forms cylinder body cylindraceous chamber; Piston, it is installed on described eccentric part in the mode being free to slide and carries out eccentric rotary motion described cylinder body is indoor together with this eccentric part; And blade, it is arranged at the blade groove that is formed on described cylinder body in the mode being free to slide, utilize the pressing force give an end to make the outer circumferential face butt of another end and described piston, by described cylinder body indoor separation, is suction chamber and pressing chamber; And
Closed container, this closed container is taken in described motor, described axle and described compression mechanical part,
Described rotary-piston type compressor is characterised in that,
In the section vertical with central shaft of described cylinder body chamber, described blade form circular shape with the end of a side described piston butt, with respect to described blade, the center line at length direction moves to pressing chamber lateral deviation at the center of this circular shape.
2. rotary-piston type compressor according to claim 1, is characterized in that,
In the section vertical with central shaft of described cylinder body chamber, at the center line of length direction, the center line with respect to the described cylinder body chamber parallel with this center line moves to described suction chamber lateral deviation described blade groove.
3. according to the rotary-piston type compressor described in claim 1 or 2, it is characterized in that,
The surface of described blade has been implemented surface treatment, makes the surface of described blade and the mother metal of this blade compare wearability and improves.
4. according to the rotary-piston type compressor described in claim 1 or 2, it is characterized in that,
The refrigeration agent using is CO
2refrigeration agent.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013083998A JP6091303B2 (en) | 2013-04-12 | 2013-04-12 | Rolling piston compressor |
| JP2013-083998 | 2013-04-12 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203796562U true CN203796562U (en) | 2014-08-27 |
Family
ID=51378778
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420172422.2U Expired - Lifetime CN203796562U (en) | 2013-04-12 | 2014-04-10 | Rotating piston type compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6091303B2 (en) |
| CN (1) | CN203796562U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106762648A (en) * | 2017-01-24 | 2017-05-31 | 广东美芝制冷设备有限公司 | Compressor, refrigeration system and automobile |
| CN109026701A (en) * | 2018-08-27 | 2018-12-18 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of compressor |
| CN111120318A (en) * | 2018-10-31 | 2020-05-08 | 广东美芝精密制造有限公司 | Compression mechanism, compressor with same, refrigeration cycle device and air conditioner |
| CN115698508A (en) * | 2020-06-22 | 2023-02-03 | 三菱电机株式会社 | Rotary compressor |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6480788A (en) * | 1987-09-21 | 1989-03-27 | Matsushita Refrigeration | Vane for enclosed type rotary compressor |
| JPH0849675A (en) * | 1994-08-04 | 1996-02-20 | Hitachi Ltd | Rotary compressor |
| JP2001207975A (en) * | 2000-01-25 | 2001-08-03 | Mitsubishi Heavy Ind Ltd | Rotary type fluid machine |
| JP4813135B2 (en) * | 2005-09-21 | 2011-11-09 | 三菱電機株式会社 | Rotary compressor |
| JP5132711B2 (en) * | 2010-04-23 | 2013-01-30 | 三菱電機株式会社 | Vane, rolling piston type single-stage rotary hermetic compressor, water heater, and vane manufacturing method |
-
2013
- 2013-04-12 JP JP2013083998A patent/JP6091303B2/en not_active Expired - Fee Related
-
2014
- 2014-04-10 CN CN201420172422.2U patent/CN203796562U/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106762648A (en) * | 2017-01-24 | 2017-05-31 | 广东美芝制冷设备有限公司 | Compressor, refrigeration system and automobile |
| CN109026701A (en) * | 2018-08-27 | 2018-12-18 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of compressor |
| CN109026701B (en) * | 2018-08-27 | 2024-03-22 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of compressor |
| CN111120318A (en) * | 2018-10-31 | 2020-05-08 | 广东美芝精密制造有限公司 | Compression mechanism, compressor with same, refrigeration cycle device and air conditioner |
| CN111120318B (en) * | 2018-10-31 | 2022-11-15 | 广东美芝精密制造有限公司 | Compression mechanism, compressor with same, refrigeration cycle device and air conditioner |
| CN115698508A (en) * | 2020-06-22 | 2023-02-03 | 三菱电机株式会社 | Rotary compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6091303B2 (en) | 2017-03-08 |
| JP2014206102A (en) | 2014-10-30 |
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| C14 | Grant of patent or utility model | ||
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| CX01 | Expiry of patent term |
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