CN100366912C - Vortex type compressor - Google Patents
Vortex type compressor Download PDFInfo
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- CN100366912C CN100366912C CNB03142497XA CN03142497A CN100366912C CN 100366912 C CN100366912 C CN 100366912C CN B03142497X A CNB03142497X A CN B03142497XA CN 03142497 A CN03142497 A CN 03142497A CN 100366912 C CN100366912 C CN 100366912C
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Abstract
Provided is a scroll compressor capable of performing a highly efficient operation, by supplying a suitable amount of lubricating oil to a back pressure chamber or a scroll even when differential pressure between discharge pressure and suction pressure is high. A lubricating oil sump 22 disposed inside the center of a bearing member 7 and a back pressure chamber 28 disposed inside the outer periphery are communicated through a lubrication passage formed of a pore 29 and a long hole 30. An oil outlet of the long hole 30 is disposed at a position opening to the back pressure chamber 28, and an oil inlet of the pore 29 is disposed at a position where the oil inlet of the pore 29 reciprocates across an annular seal member 25 by a turning operation of a turning spiral member 11 and alternately opens to the lubricating oil sump 22 and the back pressure chamber 28. Lubricating oil reserving in the lubricating oil sump 22 is intermittently supplied to the back pressure chamber 28. Therefore, the lubricating oil amount of which supply is apt to excessively increase due to high differential pressure is controlled suitably, and a highly efficient and stable operation of the scroll compressor 50 is allowed.
Description
Technical field
The present invention relates to the technology that a kind of lubricant oil that will be used for the scroll compressor of refrigerating circulatory device supplies to compression volume in right amount, relating to a kind of is refrigeration agent, for example carbon dioxide (the following CO of being of high pressure with head pressure
2) as the scroll compressor of refrigeration agent.
Background technique
Scroll compressor has low vibration, low dry sound characteristic, because the mobile of compressed fluid is unidirectional, the fluid resistance when therefore running up is little, and therefore the compression efficiency height is used widely.
As the scroll compressor of prior art, the known form that structure shown in Figure 7 is arranged.That is, scroll compressor 55 comprises seal container 1 and is configured in its inner compression mechanical part 2 and motor 3, and motor 3 is made of stator 4 and rotor 5, and live axle 6 connects and is incorporated into rotor 5.Compression mechanical part 2 meshes fixed scroll parts 10 and rotation turbination part 11 and forms a plurality of compression volumes 31, by the bent axle 9 of the front end that is positioned at live axle 6 make its rotation turbination part 11 that rotatablely moves towards the center of scrollwork on one side mobile compression volume 31 reduce its volume on one side gradually, suck thus and refrigerant gas that compress air conditioner is used etc.
In addition, opposition side at the rotation scroll vane face that rotates turbination part 11 is provided with bearing components 7, swivel bearing 13, top lubricant oil reservoir 21 and lubricant oil reservoir 22, this bearing components 7 constitutes the part of compression mechanical part 2, this swivel bearing 13 is fixed on the above-mentioned bearing components 7, and this top lubricant oil reservoir 21 and lubricant oil reservoir 22 are used for lubricated and cooling bearing 8.In addition, be provided with the back pressure chamber that has disposed rotation restraining part 12, this rotation restraining part 12 is used to prevent to rotate the rotation of turbination part 11, and this back pressure chamber 28 is communicated with top lubricant oil reservoir 21 by fuel feeding path 40.
And, the lubricant oil of top lubricant oil reservoir 21 is depressurized in supply passage 40, supply to the back pressure chamber 28 of pressing the space as middle from top lubricant oil reservoir 21 as high-pressure space, thereby carry out the lubricated of rotation restraining part 12, and, lubricant oil supplies to suction space 32 and compression volume 31 as low-voltage space from this back pressure chamber 28 by pressure adjustmenting mechanism 33, plays the effect of the slip surface of the effect of leakage of refrigerant gas in preventing to compress etc. and lubricated fixed scroll parts 10 and rotation turbination part 11.
But in the fuel feeding of existing scroll compressor structure, when the pressure reduction of high pressure side and low voltage side became big, it is many that the supply of lubricants capacity also becomes, and therefore, changes into for example CO at HFC (the plain compound of the fluorine) refrigeration agent etc. that will be used in refrigerating circulatory device etc.
2During refrigeration agent, head pressure becomes and is equivalent to CO
215 megapascal (MPa)s of supercritical pressure about very high pressure, the pressure reduction of high pressure side and low voltage side arrives about 3 times～5 times of HFC refrigeration agent greatly, therefore, produces the glut of lubricant oil, further its lubricant oil of compression brings the problem of influence for the high pressure efficient of scroll compressor.
Summary of the invention
The purpose of this invention is to provide a kind of scroll compressor, even the pressure reduction of this scroll compressor high pressure side and low voltage side is big, by also carrying out high efficiency running to back pressure chamber and compression volume appropriate amount ground supplying lubricating oil.
Another object of the present invention provides a kind of scroll compressor in addition, even this scroll compressor uses CO
2Refrigeration agent is compressed to supercritical pressure, also can realize suitable fuel feeding, can carry out high efficiency running.
In order to solve above-mentioned problem, the scroll compressor of first scheme of the present invention has fixed scroll parts, rotation turbination part, bearing components, high-pressure space, middle space, annular seal member, the fuel feeding path of pressing; These fixed scroll parts have stationary scroll blade and fixed end panel; This rotation turbination part has rotation scroll vane and round end panel, refrigerant gas is drawn into the compression volume that makes the engagement of this rotation scroll vane and said fixing scroll vane and form, rotatablely moves and refrigerant gas is compressed to head pressure by it; Above-mentioned bearing components is located at above-mentioned rotation turbination part and above-mentioned rotation scroll vane face opposition side; Above-mentioned high-pressure space is positioned at the central interior of above-mentioned bearing components, is used for storing lubricant oil under above-mentioned head pressure; Press the space to be positioned at the periphery inside of above-mentioned bearing components in the middle of above-mentioned; Above-mentioned annular seal member is divided above-mentioned high-pressure space and the above-mentioned middle space of pressing; Above-mentioned fuel feeding path is located on the above-mentioned rotation turbination part, this scroll compressor utilizes above-mentioned fuel feeding path to supply with above-mentioned lubricant oil by above-mentioned high-pressure space and the above-mentioned middle pressure difference in space of pressing, it is characterized in that, the oil export portion of above-mentioned fuel feeding path is provided in to above-mentioned middle position of pressing the space opening, and the oil-in portion of above-mentioned fuel feeding path is configured in by rotatablely moving of above-mentioned rotation turbination part crosses over the position that above-mentioned annular seal member moves back and forth, above-mentioned fuel feeding path alternately to above-mentioned high-pressure space and above-mentioned in the middle of press the space opening, carry out fuel feeding off and on.
In addition, the scroll compressor of alternative plan of the present invention, have the fixed scroll parts, the rotation turbination part, bearing components, high-pressure space, the middle space of pressing, the annular seal member, the fuel feeding path, these fixed scroll parts have stationary scroll blade and fixed end panel, this rotation turbination part has rotation scroll vane and round end panel, refrigerant gas is drawn into the compression volume that this rotation scroll vane and said fixing scroll vane is meshed and form, rotatablely move and refrigerant gas is compressed to head pressure by it, above-mentioned bearing components is located at above-mentioned rotation turbination part and above-mentioned rotation scroll vane face opposition side, above-mentioned high-pressure space is positioned at the central interior of above-mentioned bearing components, be used under above-mentioned head pressure, storing lubricant oil, press the space to be positioned at the periphery inside of above-mentioned bearing components in the middle of above-mentioned, above-mentioned annular seal member is divided above-mentioned high-pressure space and the above-mentioned middle space of pressing, above-mentioned fuel feeding path is located on the above-mentioned rotation turbination part, this scroll compressor utilizes above-mentioned fuel feeding path to supply with above-mentioned lubricant oil by above-mentioned high-pressure space and the above-mentioned middle pressure difference in space of pressing, it is characterized in that, the oil-in portion of above-mentioned fuel feeding path is provided in position to above-mentioned high-pressure space opening, and the oil-in portion of above-mentioned fuel feeding path is configured in by rotatablely moving of above-mentioned rotation turbination part crosses over the position that above-mentioned annular seal member moves back and forth, above-mentioned fuel feeding path alternately to above-mentioned high-pressure space and above-mentioned in the middle of press the space opening, carry out fuel feeding off and on.
The scroll compressor of third party's case of the present invention is in the scroll compressor of either party case of above-mentioned first, second scheme, it is characterized in that the diameter of crossing over above-mentioned oil-in portion that above-mentioned annular seal member moves back and forth or above-mentioned oil export portion is 0.2mm～ 0.5mm.
In addition, the scroll compressor of cubic case of the present invention is in the scroll compressor of either party case of above-mentioned first～third party case, it is characterized in that, what above-mentioned refrigerant gas used is carbon dioxide, is compressed to supercritical pressure.
Description of drawings
Fig. 1 is the sectional drawing of the scroll compressor of expression one embodiment of the invention.
Fig. 2 is the local amplification profile of fuel feeding path shown in Figure 1.
Fig. 3 is the plan view of the variation of the position relation that rotatablely moves of circle expression pore shown in Figure 1 and annular seal member, that be accompanied by the rotation wrap component.
Fig. 4 is portion's sectional drawing of the scroll compressor of expression another embodiment of the present invention.
Fig. 5 is the local amplification profile of fuel feeding path shown in Figure 4.
Fig. 6 is the plan view of the variation of the position relation that rotatablely moves of circle expression pore shown in Figure 4 and annular seal member, that be accompanied by the rotation wrap component.
Fig. 7 is the sectional drawing of the existing scroll compressor of expression.
Embodiment
First mode of execution of the present invention is a kind of scroll compressor, and this scroll compressor has fixed scroll parts, rotation turbination part, bearing components, high-pressure space, middle pressure space, annular seal member, fuel feeding path; These fixed scroll parts have stationary scroll blade and fixed end panel, this rotation turbination part has rotation whirling vane and round end panel, refrigerant gas is drawn into the compression volume that this rotation scroll vane and said fixing scroll vane is meshed and form, rotatablely move and refrigerant gas is compressed to head pressure by it, above-mentioned bearing components is located at above-mentioned rotation turbination part and above-mentioned rotation scroll vane face opposition side, above-mentioned high-pressure space is positioned at the central interior of above-mentioned bearing components, be used under above-mentioned head pressure, storing lubricant oil, press the space to be positioned at the periphery inside of bearing components in the middle of above-mentioned, above-mentioned annular seal member is divided high-pressure space and the middle space of pressing, above-mentioned fuel feeding path is located on the rotation turbination part, this scroll compressor utilizes above-mentioned fuel feeding path to supply with above-mentioned lubricant oil by above-mentioned high-pressure space and the above-mentioned middle pressure difference in space of pressing, the oil export portion of above-mentioned fuel feeding path is provided in to above-mentioned middle position of pressing the space opening, by rotatablely moving of above-mentioned rotation turbination part the oil-in portion of above-mentioned fuel feeding path is moved back and forth with crossing over above-mentioned annular seal member, be provided in alternately to above-mentioned high-pressure space and above-mentioned middle position of pressing the space opening.If adopt present embodiment, even then the pressure reduction of high pressure side and low voltage side is big, also can be by only at the interruption fuel feeding of oil-in portion supplying lubricating oil during to the high-pressure space opening, the adjusting of can reducing pressure effectively, therefore, can realize suitableization of fuel delivery, realize high efficiency scroll compressor.
The scroll compressor of second mode of execution of the present invention, in order to utilize the fuel feeding path and by high-pressure space and middle pressure difference supplying lubricating oil of pressing the space, and the oil-in portion of fuel feeding path is provided in position to the high-pressure space opening, the oil export portion of fuel feeding path is moved back and forth by rotatablely moving of rotation wrap component with crossing over the annular seal member, be provided in alternately to high-pressure space and middle position of pressing the space opening.If adopt present embodiment, even then the pressure reduction of high pressure side and low voltage side is big, also can be by an interruption fuel feeding at oil export portion supplying lubricating oil when the space opening is pressed in the centre, the adjusting of can reducing pressure effectively, therefore, can realize suitableization of fuel delivery, realize high efficiency scroll compressor.
The 3rd mode of execution of the present invention is in the scroll compressor of first mode of execution or second mode of execution, and the diameter that strides across above-mentioned oil-in portion that above-mentioned annular seal member moves back and forth or above-mentioned oil export portion is 0.2mm～ 0.5mm.If adopt present embodiment, be restricted to d=0.2mm by opening diameter lower limit with oil-in portion or oil export portion, the opening diameter high limit of size of oil-in portion or oil export portion is restricted to d=0.5mm, can prevent from the annular seal member to be brought damage, a kind of scroll compressor that can realize having the interruption fuel feeding of reliability and can keep high efficiency running can be provided by peristome.
The 4th mode of execution of the present invention is in the scroll compressor of first mode of execution～the 3rd mode of execution, and what above-mentioned refrigerant gas used is carbon dioxide, is compressed to supercritical pressure.When refrigeration agent uses carbon dioxide, though head pressure becomes the suction pressure that is equivalent to supercritical pressure, the pressure reduction of itself and suction pressure is excessive, but, if adopt present embodiment,, can carry out the high effective decompression of lapse rate and regulate by first～the 3rd mode of execution, supplying lubricating oil too much can be avoided, therefore the scroll compressor that fully to guarantee the running of efficient can be provided.
[embodiment]
(embodiment 1)
Fig. 1 is the sectional drawing of the scroll compressor of expression one embodiment of the invention.In illustrated scroll compressor 50, setting compressor 2 and motor 3 in the inside of seal container 1.Compression mechanical part 2 is made of fixed scroll parts 10 and rotation turbination part 11, bearing part 7 etc., these fixed scroll parts 10 have stationary scroll blade and fixed end panel, this rotation turbination part 11 has rotation scroll vane and round end panel, this bearing components 7 be arranged on rotation turbination part 11 with the opposite side of rotation scroll vane face.Motor 3 is made up of at the rotor 5 of the inboard of this stator 4 stator 4 and the free rotary ground supporting of the inboard that is fixed on seal container 1, on this rotor 5 with breakthrough status in conjunction with live axle 6.One end free rotary ground supporting of above-mentioned live axle 6 is on bearing 8, and this bearing 8 is fixed on the bearing components 7 of a part that constitutes compression mechanical part 2.Front end at the live axle 6 that is being supported by bearing 8 has bent axle 9, and this bent axle 9 carries out eccentric motion with respect to live axle 6.
In addition, by stationary scroll blade that makes fixed scroll parts 10 and a plurality of compression volumes 31 of rotation scroll vane engagement formation that rotate turbination part 11.Rotation turbination part 11 prevents its rotation by rotation restraining part 12, makes rotation turbination part 11 be rotated motion by 13 of swivel bearings by bent axle 9.Rotation whirling parts 11 move while make compression volume 31 reduce volume gradually towards the center of scrollwork, pass through for example CO of inlet holes 14 suctions as refrigerant gas from suction pipe 45
2Gas and towards center compression CO
2Gas.High CO to head pressure
2Gas is discharged from discharge tube 46 through interior of the container 16 by tap hole 15.
In addition, the other end of live axle 6 is being supported by bottom bearing 17, has positive displacement pump 18 at its front end.The lubricant oil that is stored in the bottom lubricant oil reservoir 19 of the bottom that is located at seal container 1 supplies to the top lubricant oil reservoir 21 on the top of bent axle 9 by positive displacement pump 18 through fuel supply paths 20, and above-mentioned fuel supply path 20 is located at the axle center of live axle 6.This lubricant oil is stored in after having lubricated, cooled off swivel bearing 13 in the lubricant oil reservoir 22 of position of the central interior that is located at bearing part 7, through lubricant oil reservoir 22 lubricating bearings 8, turns back to bottom lubricant oil reservoir 19.
Constitute rotation turbination part 11 a part round end panel 23 following and bearing 7 upper interior apart with having specified gap, sealing by the annular seal member 25 in the upper interior 24 that is located at bearing part 7 (groove).That is, bearing components 7 is wrapping rotation turbination part 11 under the separated state with the gap that can be rotated motion.
On bearing components 7, be provided with depressed part 26, disposing rotation restraining part 12.And, on the top of depressed part 26, back pressure chamber 28 being set in the position of the periphery inside of bearing components 7, this back pressure chamber 28 is formed by the fixed end panel 27 of fixed scroll parts 10 and round end panel 23 and bearing components 7.Lubricant oil reservoir 22 and back pressure chamber 28 can be communicated with by the fuel feeding path (as the pore 29 and the slotted hole 30 of fuel feeding path) of the inside that is located at rotation turbination part 11 (round end panel 23).And above-mentioned high-pressure space that is communicated with the lubricant oil reservoir 22 in afore mentioned rules gap and the middle space of pressing that is communicated with back pressure chamber 28 are divided by annular seal member 25.
And, interior of the container 16 is communicated with by bearing 8 and swivel bearing 13 with lubricant oil reservoir 22 and top lubricant oil reservoir 21, high-pressure space under lubricant oil reservoir 22 and 21 formation of top lubricant oil reservoir and the roughly the same pressure state of head pressure is pressed the space in the middle of depressed part 26 and back pressure chamber 28 form.Promptly, a part that supplies to the lubricant oil of lubricant oil reservoir 22 is depressurized to intermediate pressure is supplied in depressed part 26 and back pressure chamber 28 on one side through the fuel feeding path (pore 29 and slotted hole 30) with restriction effect, thereby is configured lubricating of rotation restraining part 12 grades in depressed part 26.In other words, at the scroll compressor of present embodiment etc., utilize first pressure reduction of head pressure and intermediate pressure, promptly realize by fuel feeding path supplying lubricating oil by high-pressure space and the middle pressure difference in space of pressing.
Along with accumulating of the lubricant oil that is fed into back pressure chamber 28, the pressure of back pressure chamber 28 rises.For the pressure maintenance of back pressure chamber 28 is certain, in the middle of forming, between the suction space 32 of the low-voltage space of the back pressure chamber 28 in pressure space and formation compression volume 31 pressure adjustmenting mechanism 33 is set.When the pressure that is set when the pressure ratio of back pressure chamber 28 is high, pressure adjustmenting mechanism 33 work, the lubricant oil in the back pressure chamber 28 are supplied with and are sucked space 32, and the pressure in the back pressure chamber 28 are roughly kept certain.That is, supply to as the centre and press the lubricant oil in the back pressure chamber 28 in space to supply to suction space 32 as low-voltage space through the second fuel feeding path that contains pressure adjustmenting mechanism 33.In other words, the centre is pressed the lubricant oil in space be sent to low-voltage space by second pressure reduction of intermediate pressure and suction pressure by the second fuel feeding path.
And, supply to the lubricant oil that sucks in the space 32 and be imported into compression volume 31, play the effect of the slip surface of seal action that refrigerant gas in preventing to compress etc. leaks and lubricated fixed scroll parts 10, rotation turbination part 11, bearing part 7 etc.
The suction pressure in the intermediate pressure of the head pressure of compressor and lubricant oil reservoir 22, back pressure chamber 28, suction space 32 is suitably set, but the pressure of back pressure chamber 28 is pressed against on the fixed scroll parts 10 in order to rotate turbination part 11, be set than the pressure that sucks space 32 with improving authorized pressure, in order to obtain authorized pressure, come it is adjusted by the pore with restriction effect 29 that lubricant oil reservoir 22 and back pressure chamber 28 are communicated with and the size and the pressure adjustmenting mechanism 33 of slotted hole 30.
The back pressure that is used for rotation turbination part 11 is pressed on the fixed scroll parts 10 is the second above-mentioned pressure reduction, but when this back pressure becomes big, can cause the abnormal wear of slide part and the increase of friction loss, and it is bad therefore to increase second pressure reduction.That is, back pressure is set to appropriate value and often is held certain.In addition, when head pressure uprised, (head pressure and suction pressure poor) became big because whole pressure reduction, and therefore, second pressure reduction is if certain value, and the first then above-mentioned pressure reduction becomes greatly.Therefore, be the excessive CO of first pressure reduction
2During refrigeration agent, fuel feeding is superfluous especially.For this fuel feeding surplus, the interruption fuel feeding that is formed by the fuel feeding path of the present invention can play a role effectively, below is explained.
Fig. 2 is the partial enlarged drawing of fuel feeding path shown in Figure 1.Rotation turbination part 11 its inside shown in Figure 2 have the fuel feeding path that is made of pore 29 that is communicated with and slotted hole 30, this fuel feeding path is communicated with as the lubricant oil reservoir 22 of high-pressure space with as middle back pressure chamber 28 of pressing the space in order to reduce pressure and supplying lubricating oil.And, the 29a of oil-in portion 23a upper shed below the round end panel of the pore 29 of fuel feeding path, the 29a of oil-in portion of this pore 29 rotates between a refunding at compressor, promptly during a transhipment of rotation turbination part 11 is moving, cross over 25 to-and-fro motion of annular seal member, be provided in discontinuously position as lubricant oil reservoir 22 openings of high-pressure space.
Use Fig. 3 that the action of above-mentioned oil feeding mechanism is described.Fig. 3 is the plan view of the variation that concerns of position that the circle along with the rotation turbination part of expression pore shown in Figure 1 and annular seal member rotatablely moves.The state of the round end panel 23 of rotation turbination part 11 is seen in expression from following side.In the drawings, the circle expression of outermost perimembranous is as the outer peripheral lines 35 of the bearing components 7 of the outer wall that surrounds back pressure chamber 28, and the circle expression of central part is located at the fuel feeding road 20 on the live axle 6.Between the circle of the circle of outermost perimembranous and central part, represent ring-type sealing component 25 by two double dotted line.But also representing to be located at the rotation restraining part 12 on the round end panel 23 guiding groove 34, be located on the round end panel 23 and be communicated with lubricant oil reservoir 22 and back pressure chamber 28 as the 29a of oil-in portion of fuel feeding path and slotted hole 30 and the 30a of oil export portion, keep the lip part 36 of the rotation turbination part 11 of swivel bearing 13.
In the drawings, representing with respect to rotation turbination part 11 rotatablely move, as the 29a of oil-in portion and the relative position relation that is located at the annular seal member 25 on the bearing components 7 of the opening end of pore 29.That is, the order of Fig. 3 (a)～(d) as shown by arrows, rotation turbination part 11 is rotated motion under the state with respect to outer peripheral lines 35 off-centre of back pressure chamber 28.At this moment, the interior perimembranous of annular seal member 25 forms high-pressure space, presses the space in the middle of its peripheral part forms.Therefore, the 29a of oil-in portion of pore 29 only is communicated with the lubricant oil reservoir 22 of high-pressure space when being positioned at the perimembranous of annular seal member 25 and as middle back pressure chamber 28 of pressing the space, the lubricant oil of lubricant oil reservoir 22 supplies to back pressure chamber 28 from the 29a of oil-in portion through the oil export 30a of portion.Therefore, can be just at the supplying lubricating oil during of oil-in portion under the state of Fig. 3 (b) to the high-pressure space opening.In other words, oil export portion is provided in the position of often centre being pressed the space opening, and the annular seal member is reciprocally crossed over by oil-in portion during rotatablely moving, and is provided in alternately to high-pressure space and middle position of pressing the space opening.
The intermittently connected interruption fuel feeding that becomes lubricant oil of above-mentioned fuel feeding path has the effect of the effective supply of controlling lubricant oil with decompression.In addition, pore 29 is made of the thin through hole with restriction effect, when being the state of Fig. 3 (b), having control and supply to effect (i.e. decompression control function) as the lubricants capacity of middle back pressure chamber 28 of pressing the space from lubricant oil reservoir 22 as high-pressure space.
Like this, in the scroll compressor of present embodiment, because the supply of lubricant oil is carried out discontinuously, and undertaken by pore with restriction effect, therefore compare with the scroll compressor of the example of prior art, can suppress the delivery volume of lubricant oil, carry out the supply of suitable lubricant oil.And, press the space also to be suppressed from the centre to the lubricant oil delivery volume of low-voltage space.Therefore, even use the scroll compressor of present embodiment in combination with the big refrigerant gas of pressure reduction, the adjusting of also can reducing pressure has effectively prevented the increase of fuel feeding.That is, the minimizing of volume of the cooling medium, the scroll compressor that prevents to do to compress the such idle work of lubricant oil, keeps compression efficiency, can carry out stable running than the highland are gone in the pass that can provide the refrigeration agent heating that prevents oily suction portion place to cause.
(embodiment 2)
Fig. 4 is the sectional drawing of the scroll compressor of expression another embodiment of the present invention.Fig. 5 is the local amplification profile of fuel feeding path shown in Figure 4.Present embodiment 2 is different with the foregoing description 1 on following formation.Promptly as Fig. 4 and shown in Figure 5, the fuel feeding path of present embodiment is made of slotted hole 37 with entrance part 37a and the pore 38 with the 38a of oil export portion, be used to be communicated with as the top lubricant oil reservoir 21 of high-pressure space with as middle back pressure chamber 28 of pressing the space, the 38a of oil export portion of pore 38 crosses over annular seal member 25 and constitutes discontinuously to the position of back pressure chamber 28 openings relation.
The action of above-mentioned oil feeding mechanism is described with Fig. 6.Fig. 6 is an expression pore shown in Figure 4 and the plan view of the variation of the position relation annular seal member, that rotatablely move along with one of rotation turbination part, and the figure of the state that revolves end plates 23 that rotates turbination part 11 is seen in expression from following side.In the drawings, the outer peripheral lines 35 of the back pressure chamber 28 of most peripheral circle expression bearing components 7, middle circle represents to be located at the fuel supply path 20 on the live axle 6, represents ring-type sealing component 25 with two double dot dash lines between most peripheral circle and center circle.And guiding groove 34 is the grooves that are located in order to guide rotation restraining part 12 on the round end panel 23, and lip part 36 is the flanges that keep the rotation turbination part 11 of swivel bearing 13.And slotted hole 37 is provided in a side of on the round end panel 23 with the 37a of oil-in portion of slotted hole 37 with the 38a of oil export portion of pore 38 and is communicated with the fuel feeding path of top lubricant oil reservoir 21 and back pressure chamber 28.
In Fig. 6, expression with respect to rotation turbination part 11 rotatablely move, as the 38a of oil export portion and the relative position relation that is located at the annular seal member 25 on the bearing components 7 of the opening end of pore 38.Shown in Fig. 6 (a)～(d), rotation turbination part 11 is rotated motion with the state with respect to outer peripheral lines 35 off-centre of back pressure chamber 28.At this moment, the interior perimembranous of annular seal member 25 forms high-pressure space, presses the space in the middle of its peripheral part forms.Therefore, the 38a of oil export portion of pore 38 only is communicated with when being positioned at the peripheral part of annular seal member 25 as the top lubricant oil reservoir 21 of high-pressure space with as middle back pressure chamber 28 of pressing the space, and the lubricant oil of top lubricant oil reservoir 21 supplies to back pressure chamber 28 from the 37a of oil-in portion through the oil export 38a of portion.Therefore, the 37a of oil-in portion is often to the high-pressure space opening, and the 38a of oil export portion only presses the space opening to the centre when the state of Fig. 6 (d).Therefore, only at Fig. 6 (d) but the oil export portion of state supplying lubricating oil when the space opening is pressed in the centre promptly is to carry out what is called interruption fuel feeding.
That is, above-mentioned oil feeding mechanism carries out the only connection of supplying lubricating oil disconnection control when the state of Fig. 6 (d), the effect with delivery volume of control lubricant oil during a transhipment of rotation turbination part is moving.In addition, oil feeding mechanism is the structure with pore 38 of restriction effect, when becoming the state of Fig. 6 (d), has the effect of lubricants capacity that the back pressure chamber 28 in space is pressed in inhibition in the middle of supplying to from the top lubricant oil reservoir 21 of high-pressure space.
Like this,, can suppress delivery volume, press space to be suppressed from this centre to the lubricant oil delivery volume in suction space owing to, therefore compare with the example of prior art by the suitably decompression of connection that is interrupted, supplying lubricating oil and by having the pore of restriction effect.The scroll compressor that therefore, can provide the compression efficiency height, can carry out stable running.
(embodiment 3)
In embodiment 3, the fuel feeding that forms to the aperture position of oil-in portion with by the change of aperture position with reference to Fig. 3 and the interruption control of decompression describes, in other words control describes to break-make energy rate (duty).
In Fig. 3 (d), the diameter of " X " expression ring-type sealing component 25, " Y " expression bent axle 9 be with respect to the offset of live axle 6, " Z " expression from the center of rotation turbination part 11 to the distance at the center of the 29a of oil-in portion of pore 29.Offset " Y " is identical with the past complexor (back and forth width) of annular seal member 25.
The position of the 29a of oil-in portion that represents by above-mentioned X, Y, Z, be that the 29a of oil-in portion crosses over the top to-and-fro motion of annular seal member 25 and determined by following relation to the configuration of high-pressure space opening discontinuously.
Z＝(X/2)+m (1)
Y/2≥m≥-(Y/2)(2)
And, expression in embodiment 1 scroll compressor 50, the aperture position of the 29a of oil-in portion in above-mentioned (2) formula during m=0.That is, during embodiment 1, be half of diameter " X " of annular seal member 25 from the center of rotation turbination part 11 to the distance " Z " at the center of the 29a of oil-in portion of pore 29.The 29a of oil-in portion is positioned on the elongation line at this center of direction of center move left and right of rotation turbination part 11 (or on elongation line of the eccentric direction of bent axle 9).
And, when m=0, be the 29a of oil-in portion to the state (fuel feeding state) of high-pressure space opening, fuel feeding with press to the centre space opening not the ratio of fuel feeding state (non-fuel feeding state) be approximately 50 to 50 aperture position.
In addition, in Y/2 〉=m＞0 o'clock, be the scope of the big aperture position of the ratio fuel feeding state of non-fuel feeding state, be can reduce fuel delivery, and can improve control range as the decompression rate of the ratio that high pressure is reduced to low pressure.In addition, 0＞m 〉=-(Y/2) time, be the scope of big aperture position of the non-fuel feeding state of ratio of fuel feeding state, be can increase fuel delivery and can reduce the control range of decompression rate that high pressure is reduced to the ratio of low pressure.
In other words,, can carry out the control of break-make energy rate by changing the aperture position of the oil-in 29a of portion, can be on a large scale and control the supply and the decompression of lubricants capacity effectively.Particularly, in Y/2 〉=m＞0 o'clock, can reduce pressure efficiently and regulate the decompression rate, even use CO
2The refrigeration agent that gas is such and to be compressed to high supercritical pressure, head pressure very big also can be realized suitable fuel feeding.
In addition, when m＞Y, become the state of not supplying with oil fully, when-Y＞m, become the state of any fuel feeding.Do not meet purpose of the present invention.
In addition, in embodiment 2 scroll compressor 50, identical with fuel feeding that forms by the aperture position change and decompression control with the foregoing description 1 for the aperture position of oil export portion.Promptly, if the diameter of annular seal member 25 is made as " X ", bent axle 9 is made as " Y ", the distance from the center of rotation turbination part 11 to the center of the 38a of oil export portion of pore 38 is made as " Z " with respect to the offset of live axle 6, then the 38a of oil export portion cross on the annular seal member 25 to-and-fro motion, press the position of the 38a of oil export portion of space opening can determine by the relation of above-mentioned (1) and (2) equally to the centre discontinuously.And, in embodiment 2 in the scroll compressor 50 of expression also illustration the situation of m=0.The content of the decompression control that the aperture position change of the 38a of oil export portion forms etc. is identical with the explanation of the foregoing description 1, comprises other content in its detailed description of interior omission.
(embodiment 4)
In embodiment 4, describe to the pore size of fuel feeding path and by the expenditure and pressure adjusting that its size is brought with reference to Fig. 2 and Fig. 5.The pore 29,38 of above-mentioned fuel feeding path has restriction effect, has the effect that suppresses lubricants capacity.And, produce by flow path resistance as the decompression of this restriction effect, inversely proportional with quadratic power as the internal diameter " d " of the cross-section area of pore, in direct ratio with the length " l " of pore.Therefore, when regulating restriction effect, undertaken by inner diameter d and the length l of suitably setting illustrated pore in order suitably to suppress lubricants capacity.
Its discharge capacity of size of the scroll compressor 50 of expression is that each transfers 4.0cm in the foregoing description 1 and embodiment 2
3About.If have the compressor of this discharge capacity, the size of then rotating turbination part 11 is that the diameter " D0 " shown in Fig. 3 (c) and Fig. 6 (c) is for about 7.6cm.The size of annular seal member 25 is that diameter is that 3.8cm, width are about 0.18cm in addition.And, CO
2The head pressure of refrigeration agent is about 15 megapascal (MPa)s, therefore, is used for suitably suppressing the pore size of lubricants capacity preferably about inner diameter d=0.2～0.5mm, length l=1.5～4.5mm.
And, when the inner diameter d of setting pore and length l, should be noted that following some, that is, the expenditure and pressure that (1) is produced by length " l " is regulated width than to regulate width little with the expenditure and pressure of the inversely proportional inner diameter d of the quadratic power of internal diameter " d ", and (2) are as Fig. 2 and shown in Figure 5, length " l " depends on the thickness size of relatively thinner round end panel 23, therefore, by its size is set in the narrow scope, the degrees of freedom that the expenditure and pressure that is formed by length " l " is regulated is little.
In addition, " d " also has lime light for internal diameter, (1) considers or consider from the anti-obstruction aspect with respect to dust of pore from the perforate ease of processing aspect of pore, the lower limit of the opening size of pore (being 29a of oil-in portion or the 38a of oil export portion) is preferably about diameter d=0.2mm, (2) consider from applying of pore damaging (the opening portion edge of promptly crossing over 29a of oil-in portion that the annular seal member moves back and forth or the 38a of oil export portion brings the applying of damage damaging to the annular seal member) aspect, or regulate boundary (the oil pressure rate is crossed low point) aspect from throttling and consider that the upper limit of opening size is preferably about diameter d=0.5mm.
From the foregoing description 1, embodiment 2, embodiment 3 and embodiment 4 as can be seen, for by be interrupted fuel feeding decompression control (comprise by aperture position and change the decompression control that forms) that forms and the expenditure and pressure that forms by pore control the effect that combines can to the big scroll compressor of the pressure reduction change of high pressure side and low voltage side effectively and the scope the earth fuel feeding that reduces pressure control, particularly at refrigeration agent use CO
2Scroll compressor in because can reduce pressure effectively, fuel feeding control, therefore can be described as desirable.But, even just forms decompression control, also can reduce pressure effectively, fuel feeding controls by being interrupted fuel feeding.
As mentioned above, in scroll compressor of the present invention, during rotation the rotatablely moving of turbination part, the oil-in portion of the fuel feeding path of the back pressure chamber in the lubricant oil reservoir of connection high-pressure space and middle pressure space moves back and forth on high-pressure space opening or the oil export portion process annular seal member by the fuel feeding path discontinuously and discontinuously to pressure space, centre opening, can control the essence of lubricants capacity and supply with when reducing pressure through moving back and forth on the annular seal member.In addition, obtained to suppress the effect that combines of lubricants capacity with the restriction effect that pore was had of fuel feeding path.
Such by the decompression fuel feeding control that forms by the connection that is interrupted or reach the decompression that forms by pore by the decompression fuel feeding control that forms by the connection that is interrupted and control, even with CO
2Under the situation that pressure reduction is big in the refrigeration system of refrigeration agent, also can be suitably and effectively lubricant oil is supplied to back pressure chamber or suck the space, acquisition can provide the scroll compressor that can carry out the high running of compression efficiency.
In addition, be d=0.2mm by the lower limit that makes the pore internal diameter, can obtain to improve pore for the anti-obstruction of dust and the effect of perforate ease of processing.And, be d=0.5mm by the high limit of size that makes the pore internal diameter, can prevent to damage annular seal member and lubricants capacity and suppress not enough.
Claims (4)
1. a scroll compressor has fixed scroll parts, rotation turbination part, bearing components, high-pressure space, middle space, annular seal member, the fuel feeding path of pressing; These fixed scroll parts have stationary scroll blade and fixed end panel; This rotation turbination part has rotation scroll vane and round end panel, refrigerant gas is drawn into the compression volume that makes the engagement of this rotation scroll vane and said fixing scroll vane and form, rotatablely moves and refrigerant gas is compressed to head pressure by it; Above-mentioned bearing components is located at above-mentioned rotation turbination part and above-mentioned rotation scroll vane face opposition side; Above-mentioned high-pressure space is positioned at the central interior of above-mentioned bearing components, is used for storing lubricant oil under above-mentioned head pressure; Press the space to be positioned at the periphery inside of above-mentioned bearing components in the middle of above-mentioned; Above-mentioned annular seal member is divided above-mentioned high-pressure space and the above-mentioned middle space of pressing; Above-mentioned fuel feeding path is located on the above-mentioned rotation turbination part, this scroll compressor utilizes above-mentioned fuel feeding path to supply with above-mentioned lubricant oil by above-mentioned high-pressure space and the above-mentioned middle pressure difference in space of pressing, it is characterized in that, the oil export portion of above-mentioned fuel feeding path is provided in to above-mentioned middle position of pressing the space opening, and the oil-in portion of above-mentioned fuel feeding path is configured in by rotatablely moving of above-mentioned rotation turbination part crosses over the position that above-mentioned annular seal member moves back and forth, above-mentioned fuel feeding path alternately to above-mentioned high-pressure space and above-mentioned in the middle of press the space opening, carry out fuel feeding off and on.
2. a scroll compressor has fixed scroll parts, rotation turbination part, bearing components, high-pressure space, middle space, annular seal member, the fuel feeding path of pressing; These fixed scroll parts have stationary scroll blade and fixed end panel; This rotation turbination part has circumvolution whirling vane and round end panel, refrigerant gas is drawn into the compression volume that makes the engagement of this rotation scroll vane and said fixing scroll vane and form, rotatablely moves and refrigerant gas is compressed to head pressure by it; Above-mentioned bearing components is located at above-mentioned rotation turbination part and above-mentioned rotation scroll vane face opposition side; Above-mentioned high-pressure space is positioned at the central interior of above-mentioned bearing components, is used for storing lubricant oil under above-mentioned head pressure; Press the space to be positioned at the periphery inside of above-mentioned bearing components in the middle of above-mentioned; Above-mentioned annular seal member is divided above-mentioned high-pressure space and the above-mentioned middle space of pressing; Above-mentioned fuel feeding path is located on the above-mentioned rotation turbination part; This scroll compressor utilizes above-mentioned fuel feeding path to supply with above-mentioned lubricant oil by above-mentioned high-pressure space and the above-mentioned middle pressure difference in space of pressing, it is characterized in that, the oil-in portion of above-mentioned fuel feeding path is provided in position to above-mentioned high-pressure space opening, and the oil-in portion of above-mentioned fuel feeding path is configured in by rotatablely moving of above-mentioned rotation turbination part crosses over the position that above-mentioned annular seal member moves back and forth, above-mentioned fuel feeding path alternately to above-mentioned high-pressure space and above-mentioned in the middle of press the space opening, carry out fuel feeding off and on.
3. scroll compressor as claimed in claim 1 or 2 is characterized in that, the diameter of crossing over above-mentioned oil-in portion that above-mentioned annular seal member moves back and forth or above-mentioned oil export portion is 0.2mm～ 0.5mm.
4. scroll compressor as claimed in claim 1 or 2 is characterized in that, what above-mentioned refrigerant gas used is carbon dioxide, is compressed to supercritical pressure.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP173461/2002 | 2002-06-13 | ||
| JP2002173461A JP4152678B2 (en) | 2002-06-13 | 2002-06-13 | Scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1467378A CN1467378A (en) | 2004-01-14 |
| CN100366912C true CN100366912C (en) | 2008-02-06 |
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ID=29996469
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB03142497XA Expired - Lifetime CN100366912C (en) | 2002-06-13 | 2003-06-12 | Vortex type compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4152678B2 (en) |
| CN (1) | CN100366912C (en) |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005351098A (en) * | 2004-06-08 | 2005-12-22 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| JP2007023915A (en) * | 2005-07-19 | 2007-02-01 | Matsushita Electric Ind Co Ltd | Hermetic compressor |
| JP2007170226A (en) * | 2005-12-20 | 2007-07-05 | Sanden Corp | Scroll type fluid machine |
| JP4805063B2 (en) * | 2006-08-25 | 2011-11-02 | 株式会社デンソー | Scroll compressor |
| US7878777B2 (en) | 2006-08-25 | 2011-02-01 | Denso Corporation | Scroll compressor having grooved thrust bearing |
| JP2008101559A (en) * | 2006-10-20 | 2008-05-01 | Hitachi Appliances Inc | Scroll compressor and refrigeration cycle using the same |
| WO2010070790A1 (en) * | 2008-12-15 | 2010-06-24 | パナソニック株式会社 | Scroll compressor |
| JP5178668B2 (en) * | 2009-09-11 | 2013-04-10 | 日立アプライアンス株式会社 | Scroll compressor |
| CN102477981B (en) * | 2010-11-24 | 2015-11-04 | 株式会社丰田自动织机 | Vane compressor |
| CN103195714A (en) * | 2012-01-06 | 2013-07-10 | 艾默生环境优化技术有限公司 | Compressor having flexible thrust bearing structure |
| JP5527349B2 (en) * | 2012-04-09 | 2014-06-18 | 株式会社豊田自動織機 | Vane type compressor |
| JP6302813B2 (en) * | 2014-09-30 | 2018-03-28 | 日立ジョンソンコントロールズ空調株式会社 | Scroll compressor and refrigeration cycle apparatus using the same |
| JP6896569B2 (en) * | 2017-08-29 | 2021-06-30 | 三菱重工サーマルシステムズ株式会社 | Scroll compressor and its control method and air conditioner |
| CN111133197B (en) * | 2017-08-31 | 2022-05-13 | 法雷奥日本株式会社 | Scroll compressor having a scroll compressor with a suction chamber |
| CN207795583U (en) * | 2017-12-27 | 2018-08-31 | 艾默生环境优化技术(苏州)有限公司 | Oil supply mechanism and horizontal compressor with same |
| WO2022021644A1 (en) * | 2020-07-27 | 2022-02-03 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| JP2023130601A (en) * | 2022-03-08 | 2023-09-21 | サンデン株式会社 | Scroll-type compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001073974A (en) * | 1999-09-03 | 2001-03-21 | Sanden Corp | Scroll compressor |
| JP2001304152A (en) * | 2000-04-21 | 2001-10-31 | Yamaha Motor Co Ltd | Scroll compressor |
| JP2002048078A (en) * | 2000-07-31 | 2002-02-15 | Mitsubishi Heavy Ind Ltd | Scroll compressor |
| JP2002161873A (en) * | 2000-11-30 | 2002-06-07 | Matsushita Electric Ind Co Ltd | Scroll compressor |
-
2002
- 2002-06-13 JP JP2002173461A patent/JP4152678B2/en not_active Expired - Lifetime
-
2003
- 2003-06-12 CN CNB03142497XA patent/CN100366912C/en not_active Expired - Lifetime
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001073974A (en) * | 1999-09-03 | 2001-03-21 | Sanden Corp | Scroll compressor |
| JP2001304152A (en) * | 2000-04-21 | 2001-10-31 | Yamaha Motor Co Ltd | Scroll compressor |
| JP2002048078A (en) * | 2000-07-31 | 2002-02-15 | Mitsubishi Heavy Ind Ltd | Scroll compressor |
| JP2002161873A (en) * | 2000-11-30 | 2002-06-07 | Matsushita Electric Ind Co Ltd | Scroll compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4152678B2 (en) | 2008-09-17 |
| JP2004019499A (en) | 2004-01-22 |
| CN1467378A (en) | 2004-01-14 |
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