CN101611229B - Rotary compressor - Google Patents

Abstract

An annular cylinder chamber (C1, C2) of a cylinder (21) is partitioned into an outer cylinder chamber (C1) and an inner cylinder chamber (C2) with an annular piston (22). The cylinder (21) is caused to eccentrically rotate by driving an electric motor (30), thereby changing the volumes of the outer cylinder chamber (C1) and the inner cylinder chamber (C2). The volume ratio Vr of the inner cylinder chamber (C2) to the outer cylinder chamber (C1) is set at about 0.7. In this state, the output torque of the electric motor (30) is changed in accordance with a variation in the load torque in one turn of rotation.

Description

Rotary compressor

Technical field

The present invention relates to a kind of rotary compressor, particularly relate to and be accompanied by the vibration countermeasure that load torque change is taked.Background technique

Up to now, as the rotary compressor with two cylinder chamber, for example patent documentation 1 is disclosed, and is that the eccentric rotation motion that is accompanied by annular piston makes the volume of cylinder chamber change and the compressor of compressed refrigerant.

The compressor of said patent documentation 1 comprises the cylinder with ring-type cylinder chamber and is configured in the annular piston in this cylinder chamber.Said cylinder is made up of the outside cylinder and the inboard cylinder of mutual concentric arrangement.That is to say, between this outside cylinder and inboard cylinder, be formed with cylinder chamber, this cylinder chamber is separated into outside cylinder chamber and inboard cylinder chamber by annular piston again.Said annular piston constitutes: by motoring; The outer circumferential face and the inner peripheral surface of outside cylinder in fact have only some contact and inner peripheral surface also with when in fact the outer circumferential face of inboard cylinder has only any to contact, do eccentric rotation motion with respect to the cylinder center.

Dispose outside blade in the outside of said annular piston, and, on the blade elongation line of the outside, dispose inboard blade in the inboard.Said outside blade inserts outside cylinder, is pressed towards the introversion of the footpath direction of annular piston, and tip is crimped on the outer circumferential face of annular piston.Said inboard blade inserts inboard cylinder, is pressed towards the extroversion of the footpath direction of annular piston, and tip is crimped on the inner peripheral surface of annular piston.Said outside blade and inboard blade are divided into hyperbaric chamber and low pressure chamber respectively with outside cylinder chamber and inboard cylinder chamber.And said compressor is accompanied by the eccentric rotation motion of annular piston, carries out the inflow of fluid at the low pressure chamber of each cylinder chamber, carries out the compression of fluid in the hyperbaric chamber.Patent documentation 1: Japanese publication communique spy open flat 6-288358 communique-invention existing technology problem to be solved-

Yet; Following problem can appear in the compressor of said patent documentation 1; Because the load torque change of live axle in rev; Be accompanied by the change live axle of this load torque and drive the rotating speed change of the motor rotor of this live axle, the problem of wiring direction vibration of housing of the stator of fixed motor has taken place.And the worst situation is the damage that can fracture of the pipe arrangement that is connected in housing.Summary of the invention

The present invention invents in view of above each point, and its purpose is: do in the eccentric relatively rotating rotary compressor at cylinder with two cylinder chamber and piston, suppress the generation of the vibration that is accompanied by load change in the rev.-for the technological scheme that solves existing issue-

The invention of first aspect; The compressing mechanism 20,80 that comprises cylinder 21,81a, 81b and piston 22 with two C1 of cylinder chamber, C2,82a, 82b, 87a, 87b; Make the eccentric relatively revolution of said cylinder 21,81a, 81b and piston 22,87a, 87b and make the motor 30,65 of the volume-variation of the said C1 of cylinder chamber, C2,82a, 82b, change the torque controller 50 of the output torque of said motor 30,65 corresponding to the load torque change of compressing mechanism described in the rev 20.

In the described invention, because driving cylinder 21,81a, 81b and piston 22,87a, the 87b of motor 30,65 do relative eccentric rotation motion, be accompanied by this off-centre rotation motion, two C1 of cylinder chamber, C2,82a, 82b volumes separately change.And among each C1 of cylinder chamber, C2,82a, the 82b, the fluid that the volume that is accompanied by hyperbaric chamber (pressing chamber) reduces this hyperbaric chamber is compressed.

In the rev of said compressing mechanism 20,80, also change corresponding to the load torque of the variation motor 30,65 of angle of revolution.That is to say, in each C1 of cylinder chamber, C2,82a, 82b, almost be maximum at the front and back load torque that fluid begins to spray.Therefore, under this state, because the output torque of motor 30,65 is fixed, so the rotating speed of cylinder 21,81a, 81b or piston 22,87a, 87b changes.That is to say that big if load torque becomes, then rotating speed is slack-off, and if load torque diminishes, then rotating speed accelerates.Because the change of this rotating speed is so the tangent direction of compressor housing will be vibrated.

Yet, among the present invention, because torque controller 50, the change of output torque corresponding load torque in rev of motor 30,65 and changing.Specifically, the output torque of motor 30,65 carries out reducing along with diminishing of load torque, and the change that increase big along with the change of load torque.That is to say that the output torque of control motor 30,65 makes it become the equilibrium value of load torque.Thus, the rotating speed of cylinder 21,81a, 81b or piston 22,87a, 87b is just certain basically, and the vibration that has suppressed compressor takes place.

The invention of second aspect is in the invention of first aspect, and said cylinder 21 has the C1 of ring-type cylinder chamber, C2.On the other hand, said piston 22 is to be accommodated in the said ring-type C1 of cylinder chamber, the C2, and the C1 of this cylinder chamber, C2 are divided into the annular piston 22 of the outside C1 of cylinder chamber and two cylinder chamber of the inboard C2 of cylinder chamber.

In the described invention, because the driving of motor 30 makes cylinder 21 and piston 22,52 do relative eccentric rotation motion, be accompanied by this off-centre rotation motion, C1 of outside cylinder chamber and the inboard C2 of cylinder chamber volume separately change.And among each C1 of cylinder chamber, the C2, when the increase fluid that is accompanied by the volume of low pressure chamber (suction chamber) was inhaled into, the fluid that the volume that is accompanied by hyperbaric chamber (pressing chamber) reduces this hyperbaric chamber was compressed.

This situation also is, in the rev of said compressing mechanism 20, changes corresponding to the load torque of angle of revolution motor 30, and the rotating speed of cylinder 21 or piston 22 changes.Thus, the tangent direction of compressor housing will be vibrated.Yet, among the present invention, because torque controller 50, the change of the output torque of motor 30 corresponding load torque in rev and changing.Thus, the rotating speed of cylinder 21 or piston 22 is just certain basically, and the vibration that has suppressed compressor takes place.

The invention of the third aspect is in the invention of second aspect, and the volume ratio of said inboard C2 of cylinder chamber and the C1 of outside cylinder chamber is from 0.6 to 1.0.

In the said invention, because the volume ratio of said inboard C2 of cylinder chamber and the C1 of outside cylinder chamber is from 0.6 to 1.0, so the amplitude of fluctuation of load torque just diminishes in the rev.That is to say, as shown in Figure 5, along with the diminish amplitude of fluctuation (variation) of load torque of the volume ratio Vr of inboard C2 of cylinder chamber and the C1 of outside cylinder chamber becomes big.Particularly, if below the volume ratio Vr=0.6 degree, then the amplitude of fluctuation of load torque will become extreme big.

Yet, the control of the moment of torsion of motor 30, input current through regulating input motor 30 or input voltage etc. change the output torque of motor 30.For example, big if load torque becomes, then increase input current the output torque of motor 30 is increased, and, then reduce input current the output torque of motor 30 is also diminished if load torque diminishes.At this, usually, motor 30 drives running efficiency under the certain basically condition of input current or input voltage high.That is to say that big if the variation (controlled quentity controlled variable) of input current etc. becomes, the running efficiency of motor 30 just significantly descends.

Yet among the present invention, the volume ratio Vr with inboard C2 of cylinder chamber and the C1 of outside cylinder chamber is defined in the predetermined range through the above that kind, and the variation of the load torque in the rev is diminished.Therefore, in rev, the input current of motor 30 or the variation of input voltage reduce.Thus, suppressed the reduction of the running efficiency of motor 30.

The invention of fourth aspect, be second or the invention of the third aspect in, said motor 30 is Brushless DC motors.

In the described invention, used brushless direct current (DC) motor as motor 30, compared with using the situation that exchanges (AC) motor, the running efficiency of motor 30 is high.Particularly when the change low-speed running that change is big easily that running speed is held, carry out under the situation of moment of torsion control, the decrease in efficiency of alternating current motor is big, in fact can not turn round, and d.c. motor can be kept high efficiency relatively till low speed.

The invention of the 5th aspect, be second or the invention of the third aspect in, said torque controller 50 changes the output torque of this motor 30 through input current, input voltage or the input current phase place that changes motor 30.

In the described invention, in rev, if load torque diminishes, then through reducing the output torque that input current or input voltage reduce motor 30.And big if load torque becomes, then come the output torque of increasing motor 30 through increasing input current or input voltage.Thus, the output torque of motor 30 just becomes the equilibrium value of load torque.Also have, through the phase place (making its leading or delay) of regulating input voltage, the output torque of increase and decrease motor 30 makes it change into the equilibrium value of load torque.Through the adjustment of this input current phase place, particularly improved tracing ability for the output torque of the motor 30 of load torque jumpy.

The invention of the 6th aspect, be second or the invention of the third aspect in, the annular piston 22 that said motor 30 is bound up on respect to stationary state carries out on the rotating cylinder 21.

In the described invention, cylinder 21 becomes movable side annular piston 22 and then becomes fixed side.That is to say that cylinder 21 is done eccentric revolution with respect to annular piston 22, suppress the change of the rotating speed of cylinder 21 by torque controller 50.Its result has suppressed the generation of the vibration that the rotating speed owing to cylinder 21 causes.

The invention of the 7th aspect, be second or the invention of the third aspect in, the cylinder 21 that said motor 30 is bound up on respect to stationary state carries out on the rotating annular piston 22.

In the said invention, cylinder 21 becomes fixed side annular piston 22 and then becomes movable side.That is to say that annular piston 22 is done eccentric revolution with respect to cylinder 21, suppress the change of the rotating speed of annular piston 22 by torque controller 50.Its result has suppressed the generation of the vibration that the variation owing to the rotating speed of annular piston 22 causes.

The invention of eight aspect, be second or the invention of the third aspect in, said compressing mechanism 20, one that constitutes with C1 of outside cylinder chamber and the inboard C2 of cylinder chamber is another form for the twin-stage compressed fluid of senior side of rudimentary side.

In the described invention, at first, the low-pressure fluid that is inhaled into the outside C1 of cylinder chamber is compacted into middle hydraulic fluid.This centre hydraulic fluid is inhaled into the inboard C2 of cylinder chamber again.The middle hydraulic fluid of the C2 of this inboard cylinder chamber is compacted into high-pressure liquid again.This action that connects is carried out in the rev of compressing mechanism 20, changes the load torque of motor 30 corresponding to the angle of revolution.This situation also is to make that by torque controller 50 rotating speed of cylinder 21 or annular piston 22 is certain basically, the generation of inhibition vibration of compressor.

The invention of the 9th aspect is in the invention of eight aspect, and the volume ratio of said inboard C2 of cylinder chamber and the C1 of outside cylinder chamber is 0.6 to 0.8.

In the described invention, because the volume ratio of said inboard C2 of cylinder chamber and the C1 of outside cylinder chamber is 0.6 to 0.8, so the load torque amplitude of fluctuation in the rev diminishes.That is to say that shown in figure 13, volume ratio=0.6 of the said inboard C2 of cylinder chamber and the C1 of outside cylinder chamber and 0.8 situation are compared load torque with the situation of volume ratio Vr=0.5 (1.0) amplitude of fluctuation (variation) diminishes.In addition, under the situation of volume ratio Vr=1.0, the C1 of outside cylinder chamber is identical with the volume of the inboard C2 of cylinder chamber, also just becomes so-called single-cylinder type.The present invention makes little than this single-cylinder type compressing mechanism of load torque amplitude of fluctuation in the rev.

The invention of the tenth aspect; Be in the invention of first aspect; Said cylinder 81a, 81b are made up of first cylinder 81a of the rudimentary side with the 82a of cylinder chamber, 82b and the senior side second cylinder 81b, on the other hand; Said piston 87a, 87b are to be made up of first rotary piston 87a in the 82a of cylinder chamber that is accommodated in the said first cylinder 81a and the second rotary piston 87b that is accommodated in the 82b of cylinder chamber of the said second cylinder 81b.Have, said compressing mechanism 80 constitutes through made said two rotary piston 87a, the eccentric revolution of 87b by said motor 65 again, and twin-stage compresses the fluid between said two cylinder 81a, the 81b.

In the described invention, compressing mechanism 80 constitutes so-called two cylinder type rotary compressor structures.In this compressing mechanism 80, because the driving of motor 65 makes each rotary piston 87a, 87b do eccentric rotation motion.Again because the eccentric rotation motion of this rotary piston 87a, 87b, the volume-variation of each 82a of cylinder chamber, 82b, twin-stage compressed fluid between two cylinder 81a, 81b.Specifically, at first, the low-pressure fluid that is sucked by the 82a of cylinder chamber of the first cylinder 81a is compacted into middle hydraulic fluid.The 82b of cylinder chamber that is inhaled into the second cylinder 81b is again pressed in this centre.The middle hydraulic fluid of the 82b of this cylinder chamber is compacted into high-pressure liquid again.This a succession of action is carried out in the rev of compressing mechanism 20, changes the load torque of motor 30 corresponding to the angle of revolution.This situation also is, because torque controller 50 makes that the rotating speed of each rotary piston 87a, 87b is certain basically, the vibration that has suppressed compressor takes place.

The invention of the tenth one side is in the invention aspect the said the tenth, and the volume ratio of the 82a of cylinder chamber of the 82b of cylinder chamber of the said second cylinder 81b and the first cylinder 81a is 0.6 to 0.8.

In the described invention, because the volume ratio of the 82a of cylinder chamber of the 82b of cylinder chamber of the second cylinder 81b and the first cylinder 81a is set for 0.6 to 0.8, so the load torque amplitude of fluctuation in the rev diminishes.That is to say that shown in figure 13, the inboard C2 of cylinder chamber diminishes with the amplitude of fluctuation that the situation of volume ratio Vr=0.5 (1.0) is compared load torque with the volume ratio Vr=0.6 of the C1 of outside cylinder chamber and 0.8 situation.

The invention of the 12 aspect is in the tenth or the tenth on the one hand invention, said compressing mechanism 80, and the rotational phase of rotary piston 87b of rotational phase and the second cylinder 81b that constitutes the rotary piston 87a of the first cylinder 81a differs 180 °.

In the described invention, in the first cylinder 81a, if because of the volume of the 82a of revolution cylinder chamber of rotary piston 87a reduces, the fluid of pressing in the middle of then being compressed to is ejected.The similar therewith identical moment is among the second cylinder 81b, if increase the middle hydraulic fluid that sucks from first cylinder 81a ejection because of the volume of the 82b of revolution cylinder chamber of rotary piston 87b.The middle hydraulic fluid of this suction, again since the 82b of cylinder chamber of the second cylinder 81b reduce be compressed again.The effect of-invention-

Therefore, according to the present invention, because be the output torque that changes motor 30,65 corresponding to the change of the load torque of the compressing mechanism in the rev 20,80, institute is so that the rotating speed of cylinder 21,81a, 81b or piston 22,87a, 87b obtains mitigation.Therefore, just can suppress to change the vibration generation of the compressor that causes because of rotating speed.

Also have, according to the invention of the third aspect, because be that volume ratio with inboard C2 of cylinder chamber and the C1 of outside cylinder chamber is set at predetermined range (0.6 to 1.0), so the variation of the load torque in the rev is diminished.Thus, just can reduce the change amount of the output torque of motor 30, the efficient that also just can suppress motor 30 reduces.Its result just can seek the amount of energy saving of compressor operation.

Also have,,,, just can improve the efficient of motor 30 so compare with the situation of using alternating current motor because motor 30 is to use Brushless DC motor according to the invention of fourth aspect.Therefore, just can further seek the amount of energy saving of compressor.

Also have, according to the invention of the 9th or the tenth aspect, even if in two cylinder type compound compressor structures, the volume ratio of the C1 of cylinder chamber, 82a of stipulating the C2 of cylinder chamber, 82b and the rudimentary side of senior side is in predetermined range (0.6 to 0.8).Therefore, just can reduce the variation of load torque in the rev, the efficient that also just can suppress motor 30,65 reduces.Description of drawings

Fig. 1 is the longitudinal section of the related compressor of expression first mode of execution.Fig. 2 is the sectional elevation of the related compressing mechanism of expression first mode of execution.Fig. 3 is that the related compressing mechanism of expression first mode of execution is whenever at a distance from the sectional elevation of the working condition of 90 ° of angles of revolution.Fig. 4 is the curve of the upset condition of compression moment of torsion in the expression rev.Fig. 5 is the curve of expression compression moment of torsion with respect to the upset condition of volume ratio Vr.Fig. 6 is the curve of change ratio, vibration ratio and moyor reduction amount under the expression volume ratio Vr.Fig. 7 is the longitudinal section of the related compressor of expression second mode of execution.Fig. 8 is the sectional elevation of the related compressing mechanism of expression second mode of execution.Fig. 9 is the sectional elevation of the action of the related per 90 ° of angles of revolution of compressor of expression second mode of execution.Figure 10 is the longitudinal section of the related compressor of expression the 3rd mode of execution.Figure 11 is the sectional elevation of the related compressing mechanism of expression the 3rd mode of execution.Figure 12 is the curve of expression based on the relation of the running pressure ratio of volume ratio Vr and compression efficiency.Figure 13 is the curve of expression compression moment of torsion with respect to the upset condition of volume ratio Vr.Figure 14 is the curve of expression with respect to the moment of torsion change ratio of volume ratio Vr.Figure 15 is the longitudinal section of the related compressor of expression the 4th mode of execution.Figure 16 is the sectional elevation of the related compressing mechanism of expression the 4th mode of execution.-symbol description-

1, inboard 65 87a of 82b second cylinder chamber of motor 80 compressing mechanism 81a, first cylinders (cylinder) 81b second cylinders (cylinder) 82a first cylinder chamber (cylinder chamber) (cylinder chamber) of cylinder chamber (cylinder chamber) of 60 compressor 20 compressing mechanism 21 cylinders, 22 annular pistons (piston), 30 motor, 50 controllers (moment of torsion control assembly) the C1 outside C2 of cylinder chamber (cylinder chamber) rotary piston (piston) 87b second rotary piston (piston) specific embodiment first time

Below, specify mode of execution of the present invention based on accompanying drawing.In addition, each following mode of execution is preferred example in essence, is not intended to limit suitable thing of the present invention or purposes scope of the present invention.

(first mode of execution of invention) this first mode of execution is a rotary compressor as shown in Figure 1.This compressor 1 has been taken in compressing mechanism 20 and the motor 30 that drives this compressing mechanism 20 in housing 10, constitute full enclosed type.Said compressor 1 for example is used for the refrigerant circuit at aircondition (ari condit-ioning), and compression sprays to condenser from the refrigeration agent that vaporizer sucks.

Said housing 10, be by metastomium cylindraceous 11 be separately fixed at the upper end portion of this metastomium 11 and the upper head plate 12 and the lower end sheet 13 of underpart constitutes.Suction pipe 14 runs through said upper head plate 12, and spraying pipe 15 runs through said metastomium 11.

Said compressing mechanism 20 comprises the loam cake 16 and the lower cover 17 and cylinder 21 that are fixed on the housing 10.Said cylinder 21 has the C1 of ring-type cylinder chamber, C2, is arranged between said loam cake 16 and the lower cover 17.Said loam cake 16 becomes one with the annular piston 22 that is configured in the C1 of cylinder chamber, the C2.And, constitute said cylinder 21 with respect to annular piston 22 eccentric revolutions.That is to say that in this mode of execution, cylinder 21 becomes movable side and annular piston 22 becomes fixed side, said compressing mechanism 20 constitutes this cylinder 21 and does eccentric relatively rotation motion with annular piston 22.

Said motor 30 is the brushless DC motors (DC motor) that comprise stator 31 and rotor 32.Said stator 31 is configured in the below of compressing mechanism 20, is fixed on the metastomium 11 of housing 11.On the said rotor 32, linked with this rotor 32 rotating live axles 33.This live axle 33, above-below direction runs through compressing mechanism 20, is formed with eccentric part 33a in the part that is positioned at the C1 of cylinder chamber, C2.This eccentric part 33a, it is bigger than other part to form diameter, quantitative from the axle center eccentric gauge of live axle 33.

The inside of said live axle 33, be provided with vertically extend give oil circuit (omitting diagram).Also have, said live axle 33 underparts are provided with oil feed pump 34.This oil feed pump 34 constitutes: pick up the lubricant oil that stores at housing 10 inner bottom parts, through the slide part to oil circuit supply compressing mechanism 20 of live axle 33.

Said cylinder 21 comprises outside cylinder part 24 and inboard cylinder part 25.Said outside cylinder part 24 and inboard cylinder part 25 form each other coaxial circularly, and the end links through end plate 26 and forms as one.And the said ring-type C1 of cylinder chamber, C2 are formed between the outer circumferential face of inner peripheral surface and inboard cylinder part 25 of outside cylinder part 24.Also have, the inboard of said inboard cylinder part 25, free sliding ground chimeric the eccentric part 33a of live axle 33.In addition, said cylinder 21 is processed by cast steel or aluminum alloy etc.

On said loam cake 16 and the lower cover 17, be formed with respectively and be used for the supporting driving shaft 33 free rotating bearing 16a of portion, 17a.Like this, the compressor 1 of this mode of execution just becomes live axle 33 above-below directions and runs through the C1 of cylinder chamber, C2, and the axial two side portions of eccentric part 33a is supported on the housing 10 through the 16a of bearing portion, 17a and runs through its structure.

Said annular piston 22, the diameter of outer circumferential face form forr a short time than the diameter of the inner peripheral surface of outside cylinder part 24, and the diameter of inner peripheral surface forms greatlyyer than the diameter of the outer circumferential face of inboard cylinder part 25.And said annular piston 22 constitutes off-centre and is configured in the C1 of ring-type cylinder chamber, the C2, and the C1 of this cylinder chamber, C2 are divided into outside C1 of cylinder chamber and the inboard C2 of cylinder chamber.That is to say that the said outside C1 of cylinder chamber is formed between the outer circumferential face of inner peripheral surface and annular piston 22 of outside cylinder part 24, the said inboard C2 of cylinder chamber is formed between the outer circumferential face of inner peripheral surface and inboard cylinder part 25 of annular piston 22.And the end plate 26 of said cylinder 21 constitutes first plug members of an end that stops up each C1 of cylinder chamber, C2, and loam cake 16 constitutes second plug members of the other end of each C1 of cylinder chamber of sealing, C2.

Said annular piston 22 forms: in fact outer circumferential face some contact with the inner peripheral surface of outside cylinder part 24, with the position of 180 ° of the phase differences mutually of this point of contact, in fact also only any contacts inner peripheral surface with the outer circumferential face of inboard cylinder part 25.

As shown in Figure 2, said compressing mechanism 20 comprises blade 23, and this blade 23 is separated into hyperbaric chamber C1-Hp as pressing chamber, C2-Hp with the C1 of outside cylinder chamber and the inboard C2 of cylinder chamber and separately as low pressure chamber C1-Lp, the C2-Lp of suction chamber.This blade 23 forms and runs through annular piston 22 and tabular along the rectangular of radially extending of the C1 of cylinder chamber, C2, and two ends are fixed on the outer circumferential face of inner peripheral surface and inboard cylinder part 25 of outside cylinder part 24.

Said annular piston 22 forms the C shape that a part that blade 23 can run through is cut off.At the cut-off part of this annular piston 22, be provided with and shake axle sleeve 27.This shakes axle sleeve 27, is made up of ejection side shaft cover 27A and suction side axle sleeve 27B.Said ejection side shaft cover 27A and suction side axle sleeve 27B, hyperbaric chamber C1-Hp, C2-Hp side and the low pressure chamber C1-Lp, the C2-Lp side that are positioned at separately with respect to blade 23.

Said ejection side shaft cover 27A and suction side axle sleeve 27B form the section configuration approximate half-circular, are arranged to separately plane to right form.That is to say, between the opposing side of this two axle sleeve 27A, 27B, constituted the blade groove 28 that blade 23 slides.The said axle sleeve 27 that shakes constitutes blade 23 limits in blade groove 28 advance and retreat, and the limit is shaken with respect to annular piston 22 and blade 23 and cylinder 21 one.In addition, said two axle sleeve 27A, 27B can also not be independent individualities, but the Construction integration that links together by a part.

In the said compressing mechanism 20, be accompanied by the revolution of live axle 33, annular piston 22 moves according to the order from Fig. 3 (a) to Fig. 3 (d) with each point of contact of outside cylinder part 24 and inboard cylinder part 25.That is to say that said compressing mechanism 20 constitutes the revolution along with live axle 33, outside cylinder part 24 and the 25 not rotations of inboard cylinder part, but do revolution motion around live axle 33.

On the said loam cake 16, below suction pipe 14, be formed with slotted hole shape suction port 41.This suction port 41 from axially running through loam cake 16, is communicated with the superjacent air space (low-voltage space S1) of low pressure chamber C1-Lp, C2-Lp and the loam cake 16 of each C1 of cylinder chamber, C2.Also have, on the said outside cylinder part 24, be formed with the through hole 43 that makes the low pressure chamber C1-Lp connection that sucks space 42 and the C1 of outside cylinder chamber.On the said annular piston 22, be formed with the through hole 44 that the low pressure chamber C2-Lp of the low pressure chamber C1-Lp and the inboard C2 of cylinder chamber that make the outside C1 of cylinder chamber is communicated with.

In addition, shown in the dotted line of Fig. 1, said annular piston 22 and outside cylinder part 24 are carried out chamfering corresponding to the upper top at said suction port 41 places, form wedge shape.Like this, just can carry out effectively sucking to the refrigeration agent of low pressure chamber C1-Lp, C2-Lp.

On the said loam cake 16, be formed with two ejiction openings 45.This ejiction opening 45 is axially running through loam cake 16.The lower end of this each ejiction opening 45 is in the face of each C1 of cylinder chamber, the hyperbaric chamber C1-Hp of C2, C2-Hp.On the other hand, the upper end of this each ejiction opening 45 is communicated with ejection space 46 through the ejection valve 46 of opening, closing this ejiction opening 45.

This sprays space 47, is formed between loam cake 16 and the cover plate 18.And, on said loam cake 16 and the lower cover 17, be formed with the ejection path 47a that is communicated to the following side space (high-pressure space S2) of lower cover 17 from ejection space 47.

On the other hand, on the said lower cover 17, be provided with seal ring 29.Sealing ring 29 is seated in the annular slot 17b of lower cover 17, is crimped on the lower surface of end plate 26 of cylinder 21.Also have, on the surface of contact of said cylinder 21 and lower cover 17 and the radially inner side of seal ring 29 partly import extreme pressure lubricant.Thus, seal ring 29 constitutes: utilize the pressure of lubricant oil to dwindle flexibility (compliance) mechanism of the axial clearance between the end plate 26 of lower end surface and cylinder 21 of annular piston 22.

Yet in this mode of execution, the volume V out of the C1 of outside cylinder chamber is bigger than the volume V in of the inboard C2 of cylinder chamber.Specifically, the volume ratio Vr (Vin/Vout) of said inboard C2 of cylinder chamber and the C1 of outside cylinder chamber is set at 0.7 degree.In addition, preferably this volume ratio Vr is set at 0.6 to 1.0 value.

Also have, said compressor 21 comprises the controller 50 of the torque controller of the output torque of controlling motor 30.

Said controller 50 constitutes: the change of load torque changes the output torque of motor 30 in the rev of corresponding compressing mechanism 20.This controller 50 of the angle of revolution of rotor 32 input, this controller 50 is with predefined electric current supply motor 30 to angle of revolution that should rotor 32.That is to say that controller 50 through the input current of control motor 30, changes the output torque of this motor 30.In addition, the angle of revolution of said rotor 32, identical with the angle of revolution of live axle 33.The detected checkout value of rotary sensor for example, or the value calculated from the induced voltage or the electric current of motor 30 can be used in the angle of revolution of said rotor 32.

Specifically, when the big angle of revolution of load torque, increase input current, when the little angle of revolution of load torque, reduce input current.The output torque of motor 30 is directly proportional with input current, so as long as this input current of increase and decrease is accompanied by the also just increase and decrease of output torque of its motor 30.Thus, the output torque of motor 30 is equilibrium values of load torque, so suppressed the change of the rotating speed of live axle 33 in the rev, has also suppressed the generation of vibration.

Also have, the present invention can also be angle of revolution control input voltage or the input current phase place replacement control input current according to rotor 32, changes the output torque of motor 30.For example, increase input voltage during the big angle of revolution of load torque, reduce input voltage during the little angle of revolution of load torque.Thus, the output torque of motor 30, the increase and decrease that is directly proportional with input voltage changes to the equilibrium value of load torque.Also have, through shifting to an earlier date or postpone the phase place of input current, the output torque of motor 30 will increase and decrease, and is changed to the equilibrium value of load torque.Particularly, according to the adjustment of input current phase place, improved the tracing ability of the output torque of motor 30 to load torque jumpy.

-running action-next, with reference to the running action of each this compressor 1 of figure explanation.

At first, if the said motor 30 of starting, then the revolution of rotor 32 passes to the outside cylinder part 24 and the inboard cylinder part 25 of compressing mechanism 20 through live axle 33.Thus, blade 23 moves back and forth shaking between the axle sleeve 27 (advance and retreat action), and, blade 23 with shake axle sleeve 27 and become one, shake action with respect to annular piston 22.And said outside cylinder part 24 and inboard cylinder part 25 are with respect to annular piston 22 revolution while shaking, and compressing mechanism 20 carries out the regulation compressed action.

Specifically; Among the said outside C1 of cylinder chamber; Volume at Fig. 3 (d) state low pressure chamber C1-Lp has almost reached minimum, and live axle 33 becomes the state of Fig. 3 (a), Fig. 3 (b) and Fig. 3 (c) in order to illustrated right-hand rotation from here on, along with the volume of this rotation low pressure chamber C1-Lp increases gradually.And the volume that is accompanied by this low pressure chamber C1-Lp increases, and refrigeration agent is inhaled into this low pressure chamber C1-Lp through suction pipe 14, low-voltage space S1 and suction port 41.At this moment, refrigeration agent does not just directly suck low pressure chamber C1-Lp from suction port 41, and a part gets into from suction port 41 and sucks space 42, sucks low pressure chamber C1-Lp through through hole 43 therefrom.

Said live axle circles for 33 times becomes the state of Fig. 3 (d) once more, and then the refrigeration agent to said low pressure chamber C1-Lp sucks completion.And this low pressure chamber C1-Lp has become the hyperbaric chamber C1-Hp of compressed refrigerant from this time, is cut off by blade 23 to be formed with new low pressure chamber C1-Lp.Said live axle 33 further turns round, and then in said low pressure chamber C1-Lp, repeats the suction of refrigeration agent, and on the other hand, the volume of hyperbaric chamber C1-Hp reduces, compressed refrigerant in the C1-Hp of this hyperbaric chamber.The high-pressure refrigerant of this hyperbaric chamber C1-Hp flows to ejection space 47 from ejiction opening 45, and 47a flows to high-pressure space S2 through the ejection path.

The said inboard C2 of cylinder chamber; The volume of low pressure chamber C2-Lp is almost minimum under the state of Fig. 3 (b); Live axle 33 becomes the state of Fig. 3 (c), Fig. 3 (d) and Fig. 3 (a) in order to illustrated right-hand rotation from here on, along with the volume of this rotation low pressure chamber C2-Lp increases gradually.And the volume that is accompanied by this low pressure chamber C2-Lp increases, and refrigeration agent is inhaled into this low pressure chamber C2-Lp through suction pipe 14, low-voltage space S1 and suction port 41.At this moment, refrigeration agent does not just directly suck low pressure chamber C2-Lp from suction port 41, and a part gets into from suction port 41 and sucks space 42, is inhaled into the low pressure chamber C2-Lp of the inboard C2 of cylinder chamber therefrom through through hole 43, the C1 of outside cylinder chamber and through hole 44.

Said live axle circles for 33 times becomes the state of Fig. 3 (b) once more, and then the refrigeration agent to said low pressure chamber C2-Lp sucks completion.And this low pressure chamber C2-Lp has become the hyperbaric chamber C2-Hp of compressed refrigerant from this time, is cut off by blade 23 to be formed with new low pressure chamber C2-Lp.Said live axle 33 further turns round, and then in said low pressure chamber C2-Lp, repeats the suction of refrigeration agent, and on the other hand, the volume of hyperbaric chamber C2-Hp reduces, compressed refrigerant in the C2-Hp of this hyperbaric chamber.The high-pressure refrigerant of this hyperbaric chamber C2-Hp flows to ejection space 47 from ejiction opening 45, and 47a flows to high-pressure space S2 through the ejection path.

Like this, C1 of cylinder chamber and the inboard C2 of cylinder chamber are compressed the refrigeration agent that flows to high-pressure space S2 in the outside, from spraying pipe 15 ejections, after refrigerant circuit is through condensation stroke, expansion stroke and evaporation stroke, are inhaled into compressor 1 once more.

Next, the moment of torsion control action of motor 30 is described.In addition, at this, among Fig. 3, suppose the state of 180 ° of Fig. 3 (a) expression angles of revolution, the state that Fig. 3 (b) expression angle of revolution is 270 °, the state that Fig. 3 (c) expression angle of revolution is 0 °, the state that Fig. 3 (d) expression angle of revolution is 90 °.

In the said running action, the compression moment of torsion (load torque) of the rev of live axle 33, such variation shown in Fig. 4 solid line.That is to say that under the situation of the compressor 1 of this mode of execution, near the compression moment of torsion the angle of revolution is 180 ° is for maximum, the angle of revolution is that the compression moment of torsion is minimum near reaching 270 ° near 90 °.On the other hand, shown in the dotted line of Fig. 4, under the situation of general single-cylinder type rotary compressor, the compression moment of torsion becomes maximum near 180 ° of the angles of revolution, and compression moment of torsion becomes minimum near angle of revolution 0 ° (360 °).At this; If the moment of torsion amplitude of fluctuation in the rev (compression moment of torsion minimum and maximum poor) relatively; Just can know the moment of torsion amplitude of fluctuation (about 1.1Nm) of compressor involved in the present invention 1, significant little more a lot of than the moment of torsion amplitude of fluctuation (about 2.3Nm) of single-cylinder type rotary compressor.In addition, moment of torsion change as shown in Figure 4, the running pressure ratio (condensing pressure/evaporating pressure) that in the air-conditioning that uses intergrade, takes place is about 1.6 o'clock.

The input current of said motor 30 is regulated corresponding to the change of above-described compression moment of torsion.That is to say that input current value becomes maximum when the maximum compression moment of torsion, when the minimal compression moment of torsion, become minimum.Like this, in the rev of live axle 33, the input current of motor 30 changes to maximum from minimum.Yet; The variation of this input current (controlled quentity controlled variable) ratio that is to say, and is little under the situation of single-cylinder type rotary compressor; Because the amplitude of fluctuation of compression moment of torsion is big in the rev, also increase corresponding to the change of the increase input current that compresses the change in torque amplitude.

Generally speaking, motor, the more little efficient of the variation of input current good more (efficient reduction amount is little).Thus, even if carry out the situation of identical moment of torsion control, little compared with the efficient reduction amount of the motor 30 of single-cylinder type rotary compressor compressor 1 involved in the present invention.Therefore, compressor 1 integral body can be carried out energy-saving operation.

Next, the volume ratio Vr of outside C1 of cylinder chamber and the inboard C2 of cylinder chamber and the relation that ratio is when vibrated in the moment of torsion change are described.

At first, the volume ratio Vr (Vin/Vout) of C1 of outside cylinder chamber and the inboard C2 of cylinder chamber and the relation table of moment of torsion amplitude of fluctuation are shown among Fig. 5.In this Fig. 5, represented that volume ratio Vr (Vin/Vout) is: the moment of torsion amplitude of fluctuation of five kinds of situation of 50/50=1,40/60=0.66,25/75=0.33,15/85=0.17,0/100=0.Volume ratio Vr (Vin/Vout)=0/100 promptly representes single-cylinder type rotary compressor.In addition, the running pressure ratio (condensing pressure/evaporating pressure) that when carrying out the air-conditioning of specified running, produces=about 3 o'clock each moment of torsion change shown in Figure 5.

Specifically, the moment of torsion amplitude of fluctuation, maximum under the situation of volume ratio Vr=0/100, minimum under the situation of volume ratio Vr=50/50.That is to say, learn that volume ratio Vr is more little near 1 moment of torsion amplitude of fluctuation more.Therefore, volume ratio Vr is more near 1, and the vibration that is accompanied by the moment of torsion change is also just more little.

Also have, learn the cycle (intervals between two paddy at the peak in the cycle of main moment of torsion change) of main moment of torsion change, volume ratio Vr is just short more near 1 more.For example; Cycle (c of Fig. 5) specific volume that the main moment of torsion of volume ratio Vr=50/50 changes is shorter than the cycle (b of Fig. 5) of the main moment of torsion change of Vr=25/75, and cycle (b of Fig. 5) specific volume of this main moment of torsion change is than the cycle (a) weak point of Fig. 5 of the main moment of torsion change of Vr=0/100.If the cycle of this main moment of torsion change is elongated, will slowly increase vibration, it is big that the amplitude of this vibration becomes.Generally speaking, amplitude is with the proportional increase of quadratic power in cycle (1/ frequency).

At this, the reduction magnitude relation that will change ratio, vibration ratio and moyor (motor efficiency) with respect to the moment of torsion of volume ratio Vr is illustrated among Fig. 6.Wherein, ratio is when vibrated in the moment of torsion change, and moment of torsion amplitude of fluctuation and vibration are " 1 " when volume ratio Vr=0/100, is moment of torsion amplitude of fluctuation and the vibration of representing each volume ratio Vr with ratio separately.The reduction amount of moyor is that to have suppressed the change of rotating speed to greatest extent through moment of torsion control resulting.In addition, among this Fig. 6, with solid line represent moyor (motor efficiency) the reduction amount, dot moment of torsion change than, represent the vibration ratio with dot and dash line.

Specifically, ratio is when vibrated in the moment of torsion change, all is that volume ratio Vr is more little near 1 more.Also have, the reduction amount of moyor is almost 0% minimum under the situation of volume ratio Vr=1, become big along with reducing of volume ratio Vr.Have, the reduction degree that gets cicada moyor volume ratio Vr from 1.0 to 0.6 is little again, reduces to below 0.6 but work as volume ratio Vr, and it is big that the reduction degree of moyor becomes.Like this, when volume ratio Vr between 1.0 to 0.6, in the very little scope of the reduction amount of moyor, carry out moment of torsion control, can make vibration also littler than the situation of single-cylinder type rotary compressor.

As stated, in the compressor 1 of this mode of execution, through the moment of torsion of motor 30 is controlled, compare with the situation of single-cylinder type rotary compressor being carried out moment of torsion control, the efficient that more can control motor 30 reduces.Have again, be set at 0.7, not only can in the little scope of the efficient reduction amount of motor 30, carry out moment of torsion control, further control vibration through volume ratio Vr with C1 of outside cylinder chamber and the inboard C2 of cylinder chamber.Its result can control the vibration of compressor 1, and can also carry out energy-saving operation.

Also have; In this mode of execution,, used with alternating current motor (AC motor) and compared Brushless DC motor efficiently as motor 30; So assembled and also can keep during necessary low-speed running air-conditioning intergrade of compressor involved in the present invention 1 efficiently, also just can further seek energy-conservationization.

Also have, two cylinder type rotary compressors up to now are because be to be that two inflators of 1 to 1 are arranged above and below with volume ratio Vr, so each cylinder all needs the crank mechanism of separately rotary piston and eccentric part etc.Yet compressor 1 of the present invention is in an inflator, to be divided into outside C1 of cylinder chamber and the inboard C2 of cylinder chamber, is provided with the structure of common annular piston 22, and crank mechanism needs only a cover crank mechanism, so the low cost of scheme.

Also have, through forming the situation of said cylinder 21 with aluminum alloy, because the centrifugal force during revolution reduces, thus when running up, can reduce vibration, and the amount of deflection that also can suppress live axle 33 increases.Therefore, just extensively scope is efficient and lowly turn round quiveringly.

(second mode of execution of invention) this second mode of execution like Fig. 7 and shown in Figure 8, has changed the formation of the compressing mechanism 20 in said first mode of execution.That is to say that this mode of execution constitutes that annular piston 52 becomes movable side and cylinder 21 becomes fixed side, annular piston 52 carries out the off-centre revolution with respect to cylinder 21.

Said compressing mechanism 20 comprises loam cake 16 and piston body 55.Loam cake 16 forms as one with cylinder 21.Said piston body 55 constitutes with respect to cylinder 21 eccentric rotation motions.In addition, omitted lower cover 17 in this mode of execution.

Said cylinder 21 comprises forming coaxial circular outside cylinder part 24 and inboard cylinder part 25 each other.This outside cylinder part 24 and inboard cylinder part 25 are arranged on the lower surface of end plate 26 of loam cake 16.And, between the outer circumferential face of the inner peripheral surface of this outside cylinder part 24 and inboard cylinder part 25, be formed with the C1 of ring-type cylinder chamber, C2.

Said piston body 55 comprises that the setting of end plate 51 and one is arranged on the annular piston 52 and the cylindrical piston 53 of the upper surface of this end plate 51.Said piston body 55 is formed by cast steel or aluminum alloy.Said annular piston 52, the external diameter of the ratio cylindrical piston 53 that internal diameter forms is big, and coaxial with this cylindrical piston 53.And said piston body 55 constitutes annular piston 52 and is configured in the C1 of ring-type cylinder chamber, the C2 C1 of this ring-type cylinder chamber, C2 are separated into outside C1 of cylinder chamber and the inboard C2 of cylinder chamber.That is to say that the end plate 26 of loam cake 16 constitutes first plug members of the end of each C1 of cylinder chamber of sealing, C2, the end plate 51 of piston body 55 constitutes second plug members of the other end of each C1 of cylinder chamber of sealing, C2.In addition, said cylindrical piston 53 is configured in the inboard cylinder part 25.

Also have, in this mode of execution, the volume V out of the C1 of outside cylinder chamber is bigger than the volume V in of the inboard C2 of cylinder chamber, and the volume ratio Vr (Vin/Vour) that sets inboard C2 of cylinder chamber and the C1 of outside cylinder chamber is 0.7 degree.

The live axle 33 of said motor 30 is formed with eccentric part 33a in the upper end portion, this eccentric part 33a is linked to piston body 55.That is to say, the eccentric part 33a of this live axle 33, revolution freely is embedded as in the cylindric embedding part 54 that is integrally formed in piston body 55 lower surfaces.Thus, be accompanied by the revolution of live axle 33, piston body 55 is done eccentric revolution with respect to cylinder 21.

Next, the running action of this compressor 1 is described with reference to Fig. 9.In addition, the effect of each C1 of cylinder chamber, C2 is in fact same with said first mode of execution in this running action.

That is to say; Among the C1 of cylinder chamber of the outside; The volume of low pressure chamber C1-Lp under Fig. 9 (d) state is almost minimum, from then on is changed to the volume increase of this low pressure chamber of state C1-Lp of Fig. 9 (a), Fig. 9 (b) and Fig. 9 (c) along with live axle 33 revolutions, and refrigeration agent is inhaled into low pressure chamber C1-Lp.And, said live axle 33 revs, then said low pressure chamber C1-Lp becomes hyperbaric chamber C1-Hp, and live axle 33 continues revolution, the volume reducing compressed refrigerant of then said hyperbaric chamber C1-Hp.

On the other hand; Among the said inboard C2 of cylinder chamber; The volume of low pressure chamber C2-Lp under Fig. 9 (b) state is almost minimum, from then on is changed to the volume increase of this low pressure chamber of state C2-Lp of Fig. 9 (c), Fig. 9 (d) and Fig. 9 (a) along with live axle 33 revolutions, and refrigeration agent is inhaled into low pressure chamber C2-Lp.And, said live axle 33 revs, then said low pressure chamber C2-Lp becomes hyperbaric chamber C2-Hp, and live axle 33 continues revolution, the volume reducing compressed refrigerant of then said hyperbaric chamber C2-Hp.

In this mode of execution, same with said first mode of execution, carry out moment of torsion control by 50 pairs of motor of controller 30.Therefore, compare with the situation of single-cylinder type compressor being carried out moment of torsion control, the efficient that can control motor 30 reduces, and also can seek the amount of energy saving of compressor 1.

Also have, under the situation that said piston body 55 usefulness aluminum alloys are processed, the same with first mode of execution, the amount of deflection that when running up, has suppressed vibration and live axle 33 increases, and can carry out running efficient and low vibration at wider range.Other formation, effect and effect and first mode of execution are same.

(the 3rd mode of execution of the present invention) this 3rd mode of execution, like Figure 10 and shown in Figure 11, the compressing mechanism 20 that constitutes said first mode of execution carries out the twin-stage compressed refrigerant.That is to say, the compressing mechanism 20 of this mode of execution, the C1 of outside cylinder chamber constitutes rudimentary side pressing chamber, and the inboard C2 of cylinder chamber constitutes the high pressure side pressing chamber.

Said compressor 1 is used in for example with carbon dioxide (CO ₂) be refrigeration agent, carry out the circuit refrigerant circuit that twin-stage compression one-level expands.This refrigerant circuit, although not shown, be that the order according to compressor 1, radiator (gas cooler), cistern (receiver), interstage cooler, expansion valve and vaporizer is connected by refrigerant piping.In this refrigerant circuit, from the high-pressure refrigerant of the inboard C2 of the cylinder chamber ejection of compressor 1, flow according to the order of radiator, cistern, expansion valve and vaporizer, flow into the C1 of outside cylinder chamber of compressor 1.On the other hand, in the interstage cooler, flow into that in the outside C1 of cylinder chamber compressed in the middle of the compacting cryogen, and be depressurized inflow from the part of the liquid refrigerant of cistern.In this interstage cooler, be cooled from compacting cryogen in the middle of the C1 of outside cylinder chamber.This be cooled in the middle of the compacting cryogen, return the inboard C2 of cylinder chamber and be compressed again.Repeat this circulation, for example at the evaporator cools indoor air.

The metastomium 11 that runs through the housing 10 of said compressor 1 is provided with suction pipe 14, intake channel 1a and outlet pipe 1b.Suction pipe 14 is connected in vaporizer, and intake channel 1a and outlet pipe 1b are bound up on interstage cooler.The upper end plate 12 that runs through said housing 10 is provided with spraying pipe 15.This spraying pipe 15 is connected in radiator.

On the loam cake 16 of said compressing mechanism 20, be provided with cover plate 18.In the said housing 10, the top of cover plate 18 forms high-pressure space 4a, presses space 4b in the middle of the below of lower cover 17 forms.On the said high-pressure space 4a, opening one end of spraying pipe 15, press on the 4b of space in the middle of said, opening the end of outlet pipe 1b.

Be formed between loam cake 16 and the cover plate 18, middle cavity 4c and the high pressure cavity 4d of pressing, and the middle path 4e that presses is formed in the loam cake 16.Also have, on loam cake 16 and the lower cover 17, form the sub-4f of marsupial in the periphery that is being positioned at outside cylinder part 24.Connecting intake channel 1a on the end of pressure path 4e in the middle of said, on the other hand, said sack 4f constitutes the low pressure atmosphere environment of the suction pressure that connects suction pipe 14.

The radial direction that runs through said outside cylinder part 24 is formed with the first suction port 41a, and this first suction port 41a is formed on the right side of blade 23 among Figure 11.That is to say that the first suction port 41a is interconnected the outside C1 of cylinder chamber, sack 4f and suction pipe 14.

Press the other end of path 4e in the middle of said, be formed with the second suction port 41b.This second suction port 41b is formed on the right side of blade 23, is opened on the inboard C2 of cylinder chamber, and C2 of this inboard cylinder chamber and the middle space 4b of pressure are interconnected.

On said loam cake 16, be formed with the first ejiction opening 45a and the second ejiction opening 45b.These ejiction openings 45a, 45b are from axially running through loam cake 16.The said first ejiction opening 45a, an end is positioned at the high pressure side of the C1 of cylinder chamber in the outside, and the other end is positioned at the pressure cavity 4c in the centre.The said second ejiction opening 45b, an end opening are in the high pressure side of the inboard C2 of cylinder chamber, and the other end is opened on high pressure cavity 4d.And, on the outer end of the said first ejiction opening 45a and the second ejiction opening 45b, be provided with the ejection valve 46 of leaf valve.

Press cavity 4c and the middle space 4b of pressure in the middle of said, be communicated with by the access 4g that is formed on loam cake 16 and lower cover 17.Also have, although said high pressure cavity 4d not shown, is communicated in high-pressure space 4a through the high-pressure passage that is formed on the cover plate 18.

Also have, in this mode of execution also be, the volume V out of the C1 of outside cylinder chamber is bigger than the volume V in of the inboard C2 of cylinder chamber, and the volume ratio Vr (Vin/Vout) that sets inboard C2 of cylinder chamber and the C1 of outside cylinder chamber is 0.7 degree.

In this compressor 1, if starting motor 30 is same with said first mode of execution, outside cylinder part 24 and inboard cylinder part 25 are with respect to annular piston 22 revolution while shaking.And said compressing mechanism 20 carries out the regulation compressed action.

The said outside C1 of cylinder chamber, if its volume is accompanied by the revolution of live axle 33 and increases, then low pressure refrigerant is inhaled into through the sack 4f and first suction port 42 from suction pipe 14.Have again, if live axle 33 continues revolution, the volume reducing of the outside C1 of cylinder chamber then, refrigeration agent is compressed.If pressure pressed the pressure reduction of cavity 4c to reach setting value with the centre in the middle of the pressure of the C1 of this outside cylinder chamber became regulation, ejection valve 46 is opened, and the C1 of cylinder chamber sprays to the middle cavity 4c that presses to then middle compacting cryogen from the outside, presses space 4b to flow out from outlet pipe 1b through the centre.

On the other hand, at the said inboard C2 of cylinder chamber, if its volume is accompanied by the revolution of live axle 33 and increases, then middle compacting cryogen presses the path 4e and second suction port 43 to be inhaled into from intake channel 1a through the centre.Have again, if live axle 33 continues revolution, the volume reducing of the then inboard C2 of cylinder chamber, refrigeration agent is compressed.The pressure reduction that the pressure of the C2 of this inboard cylinder chamber becomes regulation high pressure and high pressure cavity 4d reaches setting value, and ejection valve 46 is opened, and then high-pressure refrigerant sprays to high pressure cavity 4d from the inboard C2 of cylinder chamber, flows out from spraying pipe 15 through high-pressure space 4a.Like this, the compressor 1 of this mode of execution carries out refrigeration agent that in the outside C1 of cylinder chamber has been compressed again in the compressed twin-stage compression of the inboard C2 of cylinder chamber.

At this, usually, aircondition (transducer air conditioning=inverter conditioner), the running pressure ratio is higher than the frequency of zone running at about low-pressure of 1.6 to 2.0.At this, the running pressure ratio, be in the refrigerant circuit condensing pressure to the ratio of evaporating pressure.

Shown in figure 12, in the zone of the high low running pressure ratio of running frequency, the volume ratio Vr of inboard C2 of cylinder chamber and the C1 of outside cylinder chamber is high more, and compression efficiency is high more.For example, volume ratio Vr is under 0.8 the situation, and near running pressure ratio compression efficiency 1.5 is maximum, and volume ratio Vr is that the running pressure ratio is the compression efficiency maximum near 1.9 under 0.6 the situation.On the other hand, volume ratio Vr is under 0.5 the situation, and near running pressure ratio compression efficiency 2.5 is maximum, if the pressure ratio that turns round is reduced to below 2.0, compression efficiency significantly reduces.That is to say that under the situation of C1 of outside cylinder chamber and the compression of the inboard C2 of cylinder chamber twin-stage, the compression ratio of more little compressing mechanism 20 integral body of volume ratio Vr is just big more.Like this, under the low operating condition of running pressure ratio, be easy to generate the overcompression loss, compression efficiency reduces.

Next, the relation table of volume ratio Vr (Vin/Vout) and moment of torsion amplitude of fluctuation is shown among Figure 13, and the relation table of volume ratio Vr (Vin/Vout) and moment of torsion change ratio is shown among Figure 14.In these figure, moment of torsion amplitude of fluctuation and moment of torsion change ratio learns it all is that the situation specific volume of volume ratio Vr=0.6 and 0.8 is littler than the situation of Vr=0.5 and 1.Therefore, moment of torsion is equable that part of, has also just controlled vibration.In addition, moment of torsion change ratio, the moment of torsion amplitude of fluctuation that is volume ratio Vr=1 is to represent the moment of torsion amplitude of fluctuation under each volume ratio Vr situation with ratio for " 1 ".Also have, Figure 13 and Figure 14 are to be about 2 state mensuration down in the running pressure ratio.

Volume ratio Vr=1 representes the identical situation of volume of outside C1 of cylinder chamber and the inboard C2 of cylinder chamber, but this situation, and refrigeration agent is not compressed in the C1 of outside cylinder chamber and only is compressed at the inboard C2 of cylinder chamber, does not compress but single stage compression for twin-stage.That is to say that volume ratio Vr=1 is actually the same with the situation of being carried out single stage compression by up to now single-cylinder type rotary compressor.At this, the situation of volume ratio Vr=0.5, moment of torsion amplitude of fluctuation and moment of torsion change are than bigger than the situation of Vr=1.That is to say,, be necessary, still, learn as its sport efficiency as a result to have the also low situation of single-cylinder type rotary compressor than up to now by moment of torsion control control torque because vibration is big.

As stated; According to the twin-stage compressed configuration of this mode of execution, be set at 0.6 to 0.8 degree through volume ratio Vr with the inside and outside C1 of cylinder chamber, C2, compare with single-cylinder formula compressor up to now; When compression efficiency can be improved, also can control vibration.

(the 4th mode of execution of invention) this 4th mode of execution like Figure 15 and shown in Figure 16, is the twin-stage compressed configuration that has changed the compressing mechanism 20 of said the 3rd mode of execution.That is to say that the compressing mechanism of said the 3rd mode of execution 20, two C1 of cylinder chamber, C2 are formed in the same plane, but 80, two 82a of cylinder chamber of the compressing mechanism of this mode of execution, 82b lamination up and down constitutes so-called two-layer rotary compressor.

Specifically, the compressor 60 of this mode of execution, constituting is in the housing 61 of the cylindrical shape closed container of lengthwise, has taken in to comprise rudimentary side pressure the contract 80a of mechanism and senior side pressure the contract compressing mechanism 80 and motor 65 of the 80b of mechanism.In housing 61, motor 65 is arranged on the upside of compressing mechanism 80.

Said housing 61, suction pipe 62 runs through its metastomium, and spraying pipe 63 runs through its top.Spraying pipe 63, its inlet side crooked along continuous straight runs in housing 61 extends opening.

Said motor 65 is made up of stator 66 and rotor 67.Stator 66 is fixed on the inner peripheral surface of housing 61.Rotor 67 is configured in the inboard of stator 66.Central part at rotor 67 is linking live axle 70 main shaft part 71 that above-below direction extends.

Said live axle 70 constitutes live axle.On the live axle 70, be formed with first eccentric part 72 and second eccentric part 73 according to from bottom to top order.First eccentric part 72 and second eccentric part 73 form greatlyyer and be eccentric in the axle center of main shaft part 71 than the diameter of main shaft part 71.First eccentric part 72 and second eccentric part 73 are opposite each other with respect to the axle center eccentric direction of main shaft part 71.Also have, the height of aspect ratio second eccentric part 73 of first eccentric part 72 is high.

Said compressing mechanism 80, constitute according to order from bottom to top overlapping the state at back top 84, the first cylinder 81a, intermediate clapboard 86, the second cylinder 81b and preceding top 83.Taking in the second rotary piston 87b in the first cylinder 81a.

The said first cylinder 81a, for the first time rotary piston 87a, top 84, back and intermediate clapboard 84 constitute the rudimentary side pressure 80a of mechanism that contracts.The second cylinder 81b, the second rotary piston 87b, preceding top 83 and intermediate clapboard 86 constitute the senior side pressure 80b of mechanism that contracts.The rudimentary side pressure 80a of mechanism and the senior side pressure 80b of mechanism that contracts that contracts is that a kind of rotary fluid machinery that promptly shakes piston type by displacement fluid mechanism constitutes.

Shown in figure 16, the contract rotary piston 87a first time of the 80a of mechanism of rudimentary side pressure forms circular.Rudimentary side pressure is contracted first time of the 80a of mechanism on the rotary piston 87a, and having embedded can free rotating first eccentric part 72.Also have, the contract second rotary piston 87b of the 80b of mechanism of senior side pressure also forms circular.Senior side pressure is contracted on the second rotary piston 87b of the 80b of mechanism, and having embedded can free rotating second eccentric part 73.

Said each rotary piston 87a, 87b, the outer circumferential face sliding contact of inner peripheral surface and said each eccentric part 72,73, the inner peripheral surface sliding contact of outer circumferential face and each cylinder 81a, 81b.And, be formed with the 82a of cylinder chamber, 82b between the inner peripheral surface of the outer circumferential face of each rotary piston 87a, 87b and each cylinder 81a, 81b.Each rotary piston 87a, 87b, the side is provided with outstanding planar blade 74.Each blade 74 shakes that axle sleeve 75 is supported on each cylinder 81a, 81b is last between ejiction opening 89a, 89b and the suction port 88a through stating after being arranged on, the 88b.Each blade 74 is separated into high pressure side and low voltage side with said cylinder 81a, 81b.

As stated, said compressing mechanism 80, each the rotary piston 87a of revolution, the 87b that constitute by each eccentric part 72,73 shake the limit revolution at the 82a of cylinder chamber, 82b inner edge.And the rotational phase of each rotary piston 87a, 87b differs 180 ° each other.

Said rudimentary side pressure the contract second cylinder 81b of the 80b of mechanism of the first cylinder 81a and the senior side pressure of the 80a of mechanism that contracts forms internal diameter and equates each other.Rudimentary side pressure contract the 80a of mechanism the first time rotary piston 87a and the contract second rotary piston 87b of the 80b of mechanism of senior side pressure form external diameter and equate each other.Rudimentary side pressure the contract height of the second cylinder 81b of the 80b of mechanism of the senior side pressure of aspect ratio of the first cylinder 81a of the 80a of mechanism that contracts is high.

The via intermedia 90 of ring-type is formed in the said intermediate clapboard 86.Also have, on the intermediate clapboard 86, be formed with the contract ejiction opening 89a of the 80a of mechanism of rudimentary side pressure.This ejiction opening 89a is communicated with contract senior side and the via intermedia 90 of the first cylinder 81a of the 80a of mechanism of rudimentary side pressure.On the other hand, on the preceding top 83, be formed with the contract ejiction opening 89b of the 80b of mechanism of senior side pressure.This ejiction opening 89b is communicated with the senior side pressure space in high pressure side and the housing 61 of the second cylinder 81b of the 80b of mechanism of contracting.The figure that these ejiction openings 89a, 89b are provided with their outlet of switch sprays valve outward.

Said rudimentary side pressure is contracted on the first cylinder 81a of the 80a of mechanism, is formed with suction port 88a.This suction port 88a runs through the first cylinder 81a on radial direction, connecting suction pipe 62.Also have, senior side pressure is contracted on the second cylinder 81b of the 80b of mechanism, is formed with from the suction port 88b of intermediate clapboard 86 continuities.This suction port 88b, top is opened on via intermedia 90, and end openings is in second 82b of cylinder chamber.

In the bottom in the said housing 61, be formed with the oil storage chamber that stores lubricant oil.On the underpart of live axle 70, be provided with the centrifugal oil feed pump 92 that is immersed in the oil storage chamber.This oil feed pump 92 is bound up on the rudimentary side pressure of connection that in live axle 70 above-below direction extends the contract oil supply path 91 of the 80b of mechanism of the 80a of mechanism and senior side pressure that contracts.And oil feed pump 92 constitutes through oil supply path 91 and supplies with the lubricant oil in the oil storage chamber to rudimentary side pressure the contract slide part of the 80b of mechanism of slide part and the senior side pressure of the 80a of mechanism that contracts.

Also have, in this mode of execution, the volume V 2 of volume V 1 to the 2 second 82b of cylinder chamber of first 82a of cylinder chamber is big, and the volume ratio Vr (V2/V1) of second 82b of cylinder chamber and first 82a of cylinder chamber is set at 0.7 degree.

In this compressor 60, if starting motor 65, then the limit revolution is shaken on each rotary piston 87a, 87b limit in the 81a of cylinder chamber, 81b.And compressing mechanism 80 carries out the regulation compressed action.

With reference to Figure 16 this compressed action is described.Among this Figure 16, rotary piston 87a, 87b right-hand rotation shake, and the state of rotary piston 87a, 87b contact upper dead center is 0 ° of angle of revolution, and the state angle of revolution of rotary piston 87a, 87b contact lower dead centre is 180 °.At first, if be that 0 ° state turns round slightly from the angle of revolution of live axle 70, the contact position of the rotary piston 87a and the first cylinder 81a then begins to flow into refrigeration agent from suction port 88a to first 82a of cylinder chamber through the opening portion of suction port 88a for the first time.And, flow into refrigeration agent to first 82a of cylinder chamber till arriving 360 ° to the angle of revolution of live axle 70 always.

Next; Be through with under the state (360 ° of the angles of revolution of live axle 70) of first 82a of cylinder chamber inflow refrigeration agent; Live axle 70 turns round slightly; In moment of the opening portion of contact position through suction port 88a of the first time rotary piston 87a and the first cylinder 81a, in the first cylinder 81a, suck the release of refrigeration agent.And, then beginning compressed refrigerant if continue revolution from this state-driven axle 70, the refrigerant pressure in first 82a of cylinder chamber is higher than the refrigerant pressure of via intermedia 90, and the refrigeration agent that the ejection valve is pressed in the middle of opening sprays to via intermedia 90.The ejection of refrigeration agent, the angle of revolution that proceeds to live axle 70 reaches till 360 °.

On the other hand, senior side pressure is contracted among the 80b of mechanism, be accompanied by in the revolution via intermedia 90 of live axle 70 in the middle of the compacting cryogens flow into second 82b of cylinder chamber from suction port 88b.That is to say, if the contact position of the second rotary piston 87b and the second cylinder 81b through suction port 88b, then begins to flow into refrigeration agent to second 82b of cylinder chamber from middle path 90.And, compacting cryogen in the middle of second 82b of cylinder chamber flows into always till 360 ° of the live axle 70 arrival angles of revolution.

Next, accomplished in second 82b of cylinder chamber and sucked refrigeration agent, then begun compressed refrigerant if the contact position of the second rotary piston 87b and the second cylinder 81b has passed through the opening portion of suction port 88b.And,, then spray valve and open high-pressure refrigerant and spray to the space in the housing 61 from ejiction opening 89b if the refrigerant pressure in second 81b of cylinder chamber surpasses the refrigerant pressure in the space in the housing 61.The ejection of refrigeration agent lasts till that the angle of revolution of live axle 70 reaches till 360 °.Spray to the refrigeration agent in the space in the housing 61, spray to refrigerant circuit from spraying pipe 63.Like this, the compressor 60 of this mode of execution carries out refrigeration agent compressed again twin-stage compression in senior side second 82b of cylinder chamber of having compressed at rudimentary side first 82a of cylinder chamber.

This mode of execution also is that same with said the 3rd mode of execution, the relation table of the relation of volume ratio Vr (V2n/V1) and moment of torsion amplitude of fluctuation and volume ratio Vr (V2n/V1) and moment of torsion change ratio is shown among Figure 13 and Figure 14.That is to say, moment of torsion amplitude of fluctuation and moment of torsion change ratio, all specific volume is littler than the situation of Vr=0.5 and 1 than the situation specific volume of Vr=0.6 and 0.8.Therefore, the part that reduces of moment of torsion change has suppressed vibration.Even if so in the overlapping up and down twin-stage compressed configuration of the 82a of cylinder chamber, the 82b of rudimentary side and senior side; Through its 82a of cylinder chamber, the volume ratio Vr of 82b are set in 0.6 to 0.8 degree; Compare with single-cylinder formula compressor up to now; When compression efficiency can being improved, can also suppress vibration.Practicability on the-industry-

In sum, the present invention, useful as rotary compressor with two cylinder chamber that all to be volumes change along with the off-centre revolution of piston.

Claims (4)

1. rotary compressor, this rotary compressor is applied in the aircondition, it is characterized in that comprising:

Compressing mechanism (20,80) comprising: all have cylinder chamber (82a, 82b) rudimentary side first cylinder (81a) and senior side second cylinder (81b), be accommodated in first rotary piston (87a) in the cylinder chamber (82a) of said first cylinder (81a) and be accommodated in second rotary piston (87b) in the cylinder chamber (82b) of said second cylinder (81b);

Motor (30,65) carries out the off-centre revolution through making said two rotary pistons (87a, 87b), and the volume of said each cylinder chamber (82a, 82b) is changed, and the fluid between said two cylinders (81a, 81b) is carried out the twin-stage compression; And

Torque controller (50) changes the output torque that changes said motor (65) corresponding to the load torque of compressing mechanism described in the rev (20,80),

The cylinder chamber (82b) of said second cylinder (81b) is 0.6 to 0.8 with the volume ratio of the cylinder chamber (82a) of said first cylinder (81a).

2. rotary compressor according to claim 1 is characterized in that:

Said motor (65) is a Brushless DC motor.

3. rotary compressor according to claim 1 is characterized in that:

Said torque controller (50) changes the output torque of this motor (65) through input current, input voltage or the input current phase place that changes motor (65).

4. rotary compressor according to claim 1 is characterized in that:

The rotational phase of rotary piston (87b) of rotational phase and second cylinder (81b) that said compressing mechanism (80) constitutes the rotary piston (87a) of first cylinder (81a) differs 180 °.

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