CN1431401A - Enclosed rotary compressor - Google Patents

Abstract

The invention provides an enclosed rotary compressor for preventing an internal leakage from occurring due to insufficient oil volume in a cylinder in a low speed range and a suction air heating loss and an increase in discharge oil volume from occurring due to defective lubrication of sliding parts and an excessive amount of oil supplied to the cylinder in a high speed range, even when the volume of supply oil in a roller part is varied by a rotational speed. This rotary compressor comprises motors controlled at different rotational speeds. The inside of a closed container is under a suction pressure. A front part allowing lubricating oil supplied to the inner surface of the roller part to flow therein and a rear part alternately reciprocating between the front part and a suction side and temporarily holding the lubricating oil in the front part are provided on an end plate closing a roller in the cylinder.

Description

The closed type rotary compressor

Technical field

The present invention relates to closed type rotary compressor and freezing or aircondition and heat pump system, be particularly suitable under the wide range speed conditions, having the closed type rotary compressor of high-performance, high reliability and the device of refrigeration system.

Background technique

In the prior art, as the rotary compressor of the rotary compressor that is used in freezing or air-conditioning system etc., in seal container, taking in electric element with stator and rotor and the compressing member that drives by this electric element.In compressing member, be matched with the cylinder of the eccentric part of live axle free to rotately, in cylinder, do eccentric rotational motion, compress refrigerant from the rotation of the live axle of the rotatory force of electric element by transmission as working fluid.

As further describing compression stroke, the blade that is pushed to cylinder will be divided into suction chamber and pressing chamber in the cylinder, suck the cold media air of suction chamber from suction pipe in the pressing chamber compression.Compressed cold media air is discharged in the seal container, is discharged to the external refrigerating system circulation from discharge tube again.

Mostly the rotary compressor of Gou Chenging for the back pressure that makes the blade that pushes cylinder becomes high pressure, is the seal container internal pressure as head pressure like this.The supply of lubricant oil in cylinder normally by the lubricant oil supply unit of being located at the cylinder inboard, infeeds in the cylinder by the gap between cylinder and end plate.So-called end plate is the tabular component facing to the cylinder end subtend configuration with cylindrical shape; Constitute suction chamber or pressing chamber jointly by cylinder and cylinder.

When becoming head pressure in making seal container blade is applied under the situation of back pressure, as use above-mentioned lubricant oil feed mechanism, often the lubricant oil that bleeds owing to the pressure reduction in the suction chamber becomes superfluous.As to suction chamber supplying lubricating oil surplus, with the problems such as reliability reduction that produce that the compressor performance that is caused by loss on heating etc. descends and rise and cause by the electric element coil temperature.

In addition, under the situation of being interrupted the running compressor, when compressor stopped, the high temperature and high pressure gas adverse current in the seal container was gone in the vaporizer, and evaporator temperature is risen, also have make freezing. the interruption loss problem that the performance of air-conditioning system reduces.

Moreover from preventing the viewpoint of global warming, as refrigerant in the future, natural serial refrigerant receives publicity, still, though natural serial refrigerant global warming coefficient is little but still have combustibility (as isobutane.Have in use under the situation of flammable refrigerant, consider from the Security aspect, the amount (refrigerant use amount) that refrigerant is enclosed machine may be restricted.

Generally, the gas medium pressure in the seal container is high more, is storing the coolant quantity increase more of dissolving in the lubricant oil of seal container bottom.Therefore, this refrigerant amount of dissolving in of replenishing makes the coolant quantity of enclosing in the machine increase.

Thus, be the compressor of the type of head pressure for making in the seal container, because the trend that has the coolant quantity of inclosure machine to increase, it is just very difficult that use has flammable natural serial refrigerant.

For the problems referred to above, be the rotary compressor of the low pressure vessel formula of the identical pressure of compressor low voltage side (suction pressure) of making peace greatly as the pressure of making in the seal container, can enumerate disclosed rotary compressor in the special fair 07-72547 communique of day patent.

At disclosed rotary compressor shaft bearing plate inner face (cylinder side), in the every eccentric rotary of rotary-piston (cylinder) between 1 refunding, have form the interval that comprehensively is communicated with the low pressure chamber in the cylinder, with the interval of the end plate obturation of rotary-piston be communicated with the store oil recess of position dimension size in these 3 intervals, interval of rotary-piston inboard comprehensively.Constitute by this, follow the running of compressor, during moving 1 commentaries on classics of rotatingshaft revolution, lubricant oil with the proportional oil mass of recess volume, can with pressure condition irrespectively rotatingshaft per 1 change and can often a certain amount of lubricant oil be supplied with low pressure chamber, in the time of can suppressing to start etc. outside a large amount of lubricant oil outflow machine.

Supplying with the oil of store oil recess supplies with by following mechanism.At first, after the oil of the slip surface that has lubricated the live axle eccentric part is supplied with the rotary-piston inboard, supply with the lubricant oil of this rotary-piston inboard by the centrifugal action of rotatingshaft, by eccentric direction at the inboard oil film that forms of rotary-piston.This oil slick thickness depends on the oil mass of giving that feeds to the rotary-piston inboard.Therefore, few more to oil mass, promptly the motor rotary speed in the device is low more, and oil film is thin more.Particularly rotary compressor is the occasion of horizontal arrangement type, and the area that covers lubricant oil store oil recess opening diminishes, and the volumetric efficiency that is taken into the lubricant oil of store oil portion recess reduces.

From as can be known above, in above-mentioned known example, make the motor rotary speed of oil film attenuation low more, the volumetric efficiency of store oil recess that is taken into lubricant oil is low more.In addition, be under the motor low-speed conditions, to supply with the volume of the oil mass that needs as volume settings to internal lubrication with the store oil recess, under the high speed conditions of motor of oil film thickening, the oil mass that is taken into of store oil recess increases.Like this, give the oil mass surplus in cylinder, air-breathing loss on heating increases with the oil mass that is discharged to the compressor outside, has the problem of compressor performance and whole circulation performance reduction.

In addition, under the high speed conditions of motor, as the oily discharge capacity of volume settings, under the low-speed conditions of oil film attenuation for cycle performance is reduced with the store oil recess, the store oil recess is taken into low on fuel, can produce the problem of insufficient lubrication between inner leakage current and blade and rotary-piston.

Summary of the invention

Purpose of the present invention promptly is, even cause under the situation of the oil supply quantitative changeization of rotating cylinder portion inboard in the rotating speed change because of the closed type rotary compressor, the electric element low speed of compressor might as well be at a high speed, and per 1 changes and all supplies with a certain amount of oil to suction chamber.

For achieving the above object, closed type rotary compressor of the present invention is provided with in seal container: have stator and rotor electric element, have the live axle of the eccentric part of the rotation of transmitting this electric element, by the compressing member of the rotation compression working fluid of live axle eccentric part.This compressing member is provided with: have the cylinder of the cylindric inner peripheral surface of both ends open, in cylinder, be matched with the live axle eccentric part cylinder, follow the eccentric motion of this cylinder to be divided into the blade of suction chamber and pressing chamber in the cylinder, the end plate of inaccessible cylinder opening, via the oil supply mechanism of supplying lubricating oil in the driving axial cylinder, have the front portion that is used for being taken into the lubricant oil that supplies to the cylinder inboard and mutual space and the suction chamber that is communicated with in the cylinder inboard, and have the lubricant oil feed mechanism at the rear portion that the lubricant oil to the front portion come keeps.

Description of drawings

Fig. 1 is that the horizontal arrangement type of first embodiment of the invention shakes the piston compressor sectional arrangement drawing.

Fig. 2 is the A-A sectional drawing of Fig. 1.

Fig. 3 is the action specification figure of the compressing member of Fig. 1.

Fig. 4 be first embodiment of the invention shake piston compressor major component explanatory drawing.

Fig. 5 is the B-B sectional drawing of Fig. 4.

Fig. 6 be second embodiment of the invention shake piston compressor major component explanatory drawing.

Fig. 7 is the C-C sectional drawing of Fig. 6.

Fig. 8 be third embodiment of the invention shake piston compressor major component explanatory drawing.

Fig. 9 is the D-D sectional drawing of Fig. 8.

Figure 10 is the recess enlarged view on every side of Fig. 9.

Figure 11 be fourth embodiment of the invention shake piston compressor major component explanatory drawing.

Figure 12 be fifth embodiment of the invention shake piston compressor major component explanatory drawing.

Figure 13 is the freeze cycle pie graph of the refrigerating plant of sixth embodiment of the invention.

Figure 14 is the sectional arrangement drawing that the horizontal arrangement type of seventh embodiment of the invention shakes the piston type two stage compressor.

Figure 15 is the oil supply mechanism enlarged view that horizontal arrangement type shown in Figure 14 shakes the piston type two stage compressor.

Embodiment

Bottom is described in Figure various embodiments of the present invention.And, among each embodiment below second embodiment, economize a part of omitting, and save duplicate explanation with the identical formation of first embodiment.

At first, with Fig. 1～Fig. 5 first embodiment of the invention is described.The closed type rotary compressor of present embodiment is disposing the live axle 4 of electric element, compressing member and binding in seal container 6.In addition in the present embodiment, make these seal container 6 interior suction pressures lower than head pressure.

Electric element has stator 7 and rotor 5.Compressing member has compressing mechanism and oil supply mechanism.The main bearing 2 that shakes piston 8, is jammed in cylinder 1 two ends that compressing mechanism is disposed in this cylinder 1 by the cylinder 1 with cylindric inner peripheral surface 1a, rotationally constitutes with supplementary bearing 3.Live axle 4 is fixed on the rotor 5 of electric element and to compressing member transmission driving force.By the eccentric part 4a eccentric rotary of live axle 4, shake piston 8 in cylinder 1 inner eccentric rotary.

Oil supply mechanism, describe in detail subsequently, but mainly be, be accompanied by the volume-variation of cylinder 1 1c of hole portion that the discrepancy by blade part 8b end causes, be admitted to rail 19 by discharge fluid one-way valve (ダ ィ ォ one De) 18 from sucking the lubricant oil that solution one-way valve (ダ ィ ォ one De) 17 flows into.Lubricant oil by rail 19 is supplied with enters in the supplementary bearing 3, infeeds in each bearing from the spiral goove 20 of being located at live axle 4 surfaces.

The following formation that compressing mechanism is described in detail in detail.The opening portion at the two end part of the cylindric inner peripheral surface 1a of main bearing 2 and the inaccessible at least cylinder 1 of supplementary bearing 3.In the present embodiment, cylinder 1 is fixed in main bearing 2.Main bearing 2 and supplementary bearing 3 have the 2a of bearing portion, 3a, rotatably support rotatingshaft 4 in its central authorities of part that correspond respectively to the cylindric inner peripheral surface 1a of cylinder 1.In addition, main bearing 2 and supplementary bearing 3, the rotatingshaft of live axle 4 (part beyond the eccentric part 4a) consistently is fixed in cylinder 1 with the central shaft of the cylindric inner peripheral surface 1a of cylinder 1.The peripheral part of main bearing 2 is fixed in seal container 6, is also fixing the stator 7 of electric element in seal container 6.

On live axle 4, eccentric part 4a is set in the part of the cylindric inner peripheral surface 1a that is positioned at cylinder 1.That is, allocate the cylindric inner peripheral surface of the 8a of cylinder portion that shakes piston 8 rotationally at the cylindric outer circumferential face of this eccentric part 4a.Decide each size slightly with a gap between the cylindric inner peripheral surface 1a of the cylindric outer circumferential face of the 8a of cylinder portion and cylinder 1.

In addition, the cylindric outer circumferential face at the 8a of cylinder portion is provided with blade part 8b.In the outside of the cylindric inner peripheral surface 1a of cylinder 1, the 1b of cylinder hole portion that has with the central shaft of the central axes of cylindric inner peripheral surface 1a is set.Cylinder axis one side of the 1b of cylinder hole portion and an opposite side are connected with the 1c of another hole portion that is located at the 1b of the cylinder hole portion outside with the cylindric inner peripheral surface 1a of cylinder 1 respectively.Blade part 8b inserts cylinder hole 1b of portion and the 1c of hole portion, but between blade part 8b and the 1b of cylinder hole portion, clip the slide member 9 of cylinder face that blade part 8b has assembled the planar surface portion with the planar surface portion that is connected to blade part 8b slidably and has been connected to the cylinder face of the 1b of cylinder hole portion slidably.Its result, blade part 8b can carry out towards the motion of the advance and retreat of the central shaft of the 1b of cylinder hole portion with around the swing movement of central shaft.The front end of blade part 8b moves in the 1c of hole portion, can not extract from the 1b of cylinder hole portion, also can not interfere with cylinder 1.

Owing to have above formation, when live axle 4 being rotated, shake piston 8 and promptly in cylinder 1, follow the revolution motion that shakes together with eccentric part 4a by electric element.

Fig. 3 represents that live axle 4 revolutions shake the figure of the motion of piston 8 when moving 60 °.The 8a of cylinder portion, along with the rotational motion of eccentric part 4a, revolution motion is done at its center.Blade part 8b, often carry out towards the 1b of cylinder hole portion central axis direction, around the central shaft of the eccentric part 4a swing movement of some angles only.During blade part 8b motion, promptly carry out towards the sealing in gap between the advance and retreat motion of the central shaft of the 1b of cylinder hole portion and the blade part 8b when the swing movement of its central shaft and the 1b of cylinder hole portion, seal and keep by inserting slide member 9 between blade part 8b and the 1b of cylinder hole portion.

Thereby, by cylinder 1, the combination of shaking piston 8, main bearing 2, supplementary bearing 3 and slide member 9, constituted as confined space pressing chamber 10 (Fig. 3 oblique line part) and as the suction chamber 11 that sucks the space.Be accompanied by the rotation that makes live axle 4 by electric element, be concatenated to form the increase and decrease of its volume shown in Figure 3.In whole Fig. 3 (a)～(f), form pressing chamber 10.

Constitute by this, comply with following being compressed as the cold media air of working fluid.At first, cold media air, suck in the seal container 6 from the suction pipe 12 that is installed on seal container 6, after suction path 13, be inhaled into that (suction chamber 11 is present in the suction chamber 11, behind (a) θ of crossing Fig. 3=0 °, stop up the state of suction port 1d shown in Fig. 3 (b) θ=60 ° like that by the 8a of cylinder portion) to the state of crossing Fig. 3 (f) θ=300 ° of such inaccessible exhaust port 3b shown in Fig. 3 (a).With the volume reducing while of pressing chamber 10, cold media air is compressed.Cold media air from the exhaust port 3b that is located at supplementary bearing 3 discharges is discharged to by supplementary bearing 3 and discharge cap 14 formed discharge chamber 3c.Then, compressed cold media air is discharged to outside the seal container 6 from the discharge tube 15 that runs through seal container 6.

Like this, in the present embodiment, in a single day the cold media air that particularly constitutes by suction pipe 12 sucks in the seal container, in the seal container 6 suction pressure.At this moment, the cold media air that is compressed by pressing chamber 10 is not directly to be discharged in the seal container 6, but by discharge chamber 3c, outside discharge tube 15 is discharged to seal container 6.

In the seal container 6 for suction pressure thereby following advantage is arranged.

(1) reduced by the heating of compressed high temperature refrigerant to electric elements, owing to the cooling by the low temperature cold media air, rotor 5 reduces with the temperature of stator 7, is expected to improve moyor, improves overall performance.

(2) become suction pressure because the 8a of cylinder portion is inboard, no longer include the supply that pressure reduction from the 8a of cylinder portion inner face to suction chamber 11 causes superfluous oil, be expected to improve compressor performance.

(3) owing to be the refrigerants such as fluorine Lyons that have with the intermiscibility of lubricant oil, pressure is low, and the ratio of the cold media air that dissolves in oil is few, owing to be difficult for locating to cause that at bearing etc. the cold media air foaming finds, so can improve reliability.In addition, as future competitive new cooling media have a flammable natural serial refrigerant (isobutane, propane etc.), the refrigerant consumption reduces, and can improve Security.

(4) owing to reducing the pressure-bearing of seal container 6, so be expected to realize thin-wall light-weighted.

In addition, shake piston shape compressor shown in the present embodiment, be used in the structure that becomes suction pressure in the seal container easily.Because cylinder and blade are integrated, with regard to not needing as the rotary compressor that cylinder and blade branch are done and the back pressure higher to the blade effect owing to blade being pressed on the cylinder.

Bottom describes the oil supply mechanism of compressor section in detail.In Fig. 1, by the rotation of live axle 4, the blade part 8b motion of in the 1c of hole portion, advancing and retreat, the volume-variation among the 1c of hole portion.This volume-variation causes pumping action (being the blade oil feed pump later on), makes the lubricant oil 16 store in the bottom of seal container 6 attract from sucking fluid one-way valve 17, by discharging fluid one-way valve 18, rail 19, is drawn onto live axle 4.And, the spiral goove 20 by being located at live axle 4 peripheries, return seal container 6 after having lubricated supplementary bearing 3, eccentric part 4a, main bearing 2 by the lubricant oil 16 that picked up.

The lubricant oil 16 that has lubricated eccentric part 4a flows out to the 8a of cylinder portion inner face side.For example, even cause cold media air foaming by lubricant oil 16 by spiral goove 20, the cold media air that has foamed, the bleeder hole 4b from facing to the outer circumferential face upper shed of the eccentric part 4a of the inner face of the 8a of cylinder portion discharges by the exhaust port 4c that is located at live axle 4 inside.

In addition, the high pressure refrigerant gas that bleed cylinder portion 8a inboard from pressing chamber 10, by on face, being provided with opening portion and being communicated with the intercommunicating pore 4c of exhaust port 4c, be discharged to seal container 6 by the exhaust port 4c that is located at live axle 4 inside facing to the main bearing 2 of eccentric part 4a and supplementary bearing 3.

Here, lubricant oil 16 stable supplyings that are fed on the 8a of the cylinder portion inner face formation in the cylinder 1 has been described.In Fig. 3,, be provided with the notch part 8c of side opening in the 8a of cylinder portion at the 8a of cylinder portion end face.On the end plate of supplementary bearing 3, be to and from the end face notch part 8c of the 8a of cylinder portion that is communicated with the cylinder 8a of portion inner space and the position of suction chamber alternately, be provided with oil groove 21 as the recessed recess in end plate plane.Being to and from position on the end plate of supplementary bearing 3 of the 8a of cylinder portion end face notch part 8c and suction chamber alternately, is not the tap hole 3d side in cylinder 1, but in inlet hole 1d side.That is, the position on the end plate of its supplementary bearing 3 is the position that is communicated with the cylinder 8a of portion inner space and suction chamber 11.

Lubricant oil 16 on the 8a of the feed roller portion inner face by notch part 8c guiding, is being supplied with the oil groove 21 of supplementary bearing 3 with notch part 8c subtend position.Then, to suction chamber 11 openings, the lubricant oil 16 in the oil groove 21 is promptly supplied with suction chamber 11 as oil groove 21.

Utilize Fig. 4 and Fig. 5 to be described in detail.Lubricant oil 16 between the eccentric part 4a of 8a of feed roller portion and live axle 4 has not only covered the inner face of the 8a of cylinder portion, and owing to be accompanied by the centrifugal action that live axle 4 rotates, lubricant oil 16 productive sets at eccentric part 4a facing on the face of supplementary bearing 3.By the lubricant oil 16 importing oil grooves 21 of notch part 8c with its delay.One-tenth covers the state of oil groove 21 corresponding to notch part 8c scope, notch part 8c.

Constitute by above-mentioned, because oil groove 21 is borrowed and is communicated with supplying lubricating oil 16 with the notch part 8c that is located at the 8a of cylinder portion end face, even the oil mass of the lubricant oil 16 in week is less in the 8a of feed roller portion, oil groove 21, the lubricant oil 16 that is gathered importing by its anterior notch part 8c covers comprehensively, because of can slick and slyly being taken into lubricant oil, improving the volumetric efficiency that oil groove 21 is taken into lubricant oil to oil groove 21.Its result, even under the situation that the oil mass in the different cylinder 8a of portion because of rotational velocity changes, but also revolution all has the supply suction chamber of a certain amount of lubricant oil.Promptly, can prevent low velocity zone by cylinder 1 in the inside leakage of oil that causes of low on fuel and slide member and cylinder hole portion insufficient lubrication, high velocity to the excessive air-breathing loss on heating that causes of suction chamber fuel feeding with discharge oil mass and increase, can be provided at the closed type rotary compressor of high-performance high reliability under the speed conditions of wide range.

Notch part 8c because (being roughly suction pressure) is not connected with oil groove 21 when the pressure of pressing chamber does not rise, can make the unlikely deterioration of sealing of the 8a of cylinder portion end face.

Secondly, utilize Fig. 6 and Fig. 7 that second embodiment of the invention is described.In the present embodiment, at the end face of the 8a of cylinder portion, make bight facing to the face of eccentric part 4a along establishing recessed step-like annular ditch 8d full week.Annular groove 8d has reduced the area of contact of the 8a of cylinder portion to eccentric part 4a, and the effect that alleviates contact resistance is arranged.As shown in Figure 7, not only even supplementary bearing 3 sides of the 8a of cylinder portion to main shaft 2 sides, as are established annular ditch 8d, can further reduce contact resistance.

From the lubricant oil 16 of this annular ditch 8d feed roller 8a of portion inner face, because the centrifugal action of following live axle 4 to rotate, the eccentric direction that is directed in the annular ditch 8d gathers.On the end plate of supplementary bearing 3, when the oil groove 21 of the position when being located at annular ditch 8d with suction chamber 11 mutual contacts is connected with annular ditch 8d, the lubricant oil 16 that imports annular ditch 8d is supplied with oil groove 21.Then, to suction chamber 11 openings, the lubricant oil 16 in the oil groove 21 is supplied with suction chamber 11 as oil groove 21.

Be made of above, even the oil mass of lubricant oil 16 in week is less in the 8a of feed roller portion, because oil groove 21 covers for being in the lubricant oil 16 that gathers importing among its anterior notch part 8c comprehensively, oil groove 21 can improve the volumetric efficiency that is taken into lubricant oil.In addition, owing to establish annular ditch 8d in the 8a of cylinder portion end face both sides, reduced area of contact with the major-minor bearing face, the pattern of the wall thickness thickening of the 8a of cylinder portion cylindrical part (such as, with external diameter in the same cylinder shape change cylinder portion, live axle eccentric part external diameter, reduce the occasion of the minimum cylinder volume of compressor with offset) compressor in, obtain with first embodiment's same function effect in, can reduce the skimming wear of the 8a of cylinder portion end face.

Bottom illustrates third embodiment of the invention with Fig. 8～Figure 10.In the present embodiment, the 8a of cylinder portion on the end plate of supplementary bearing 3 is inboard to be opened wide, and establishes recess 22 in the position that the eccentric motion along with the 8a of cylinder portion becomes the part of suction chamber.Recess 22 has the shape that reduces from the lateral central direction at the radial direction of cylinder 1 from the end face of supplementary bearing 3 (with reference to Fig. 9) degree of depth h.

Owing to have such recess 22, supply to the lubricant oil 16 of cylinder portion 8a inboard, the 8a of the cylinder portion inboard on cylinder 1 one side end faces of being located at supplementary bearing 3 is to and from the recess 22 of position alternately with suction chamber 11, when being communicated with the 8a of cylinder portion inboard, is supplied with recess 22.Then, to suction chamber 11 openings, just the lubricant oil in the recess 22 16 is supplied with suction chamber 11 as recess 22.

Here, recess 22 has the store oil portion that front portion its degree of depth h that relative lubricant oil 16 enters changes.In the time of oil slick thickness thickening in the 8a of cylinder portion degree of depth h shoal, promptly since the direction degree of depth h of the thickness thickening of the lubricant oil 16 in the 8a of cylinder portion of the centrifugal action of the 8a of cylinder portion gathering diminish, therefore because following effect is arranged, oil mass increases in the cylinder 8a of portion because rotating speed increases, during the oil slick thickness thickening, comparing under the situation of the constant recess of degree of depth h, the oil mass of supplying with recess 22 is being changed reduce.

The effect of this store oil portion, the inner face of the 8a of cylinder portion, with the bottom surface (in Fig. 9, face) of recess 22 in the cylinder 1 radial direction outside, be roughly the same position in the radial direction position of cylinder 1.Comparing opening portion, changing by the section configuration of the store oil portion that becomes the rear portion (from the end sheet surface negative area of supplementary bearing 3) as the front portion of recess 22, help getting oil thereby big opening portion is set, store oil portion can be set at volume corresponding to oil slick thickness.The recess of the shape narrow at opening portion, that degree of depth h is big, residual lubricant oil becomes many, can not reach purpose originally in the recess.Therefore, as present embodiment, relatively opening portion changes store oil portion volume at the lubricating oil oil film thickness direction, can prevent infeeding the air-breathing loss on heating that too much causes to oil mass in the suction chamber and increasing the cycle performance that causes by the oil mass of discharging and reduce in high velocity thus.

Think and carry out the volume that the minimum necessary fuel delivery of low velocity zone internal lubrication is set recess 22, can avoid low on fuels cause in the low velocity zone suction chamber 11 inside leakage of oil and the insufficient lubrication of slide member 9 and the 1b of cylinder hole portion.

From the above mentioned, use the hermetic type compressor of present embodiment can be under the speed conditions of wide range, can realize high-performance and obtain high reliability.

Above-mentioned recess 22 is got the shape that the depth direction basal area changes; Other, the degree of depth and the basal area variation of vertical aspect etc. all can obtain the same function effect so long as oil slick thickness when thickening, is supplied with the shape that the oil mass increment rate of recess diminishes.

Bottom illustrates fourth embodiment of the invention with Figure 11.In Figure 11, be to and from position on the end plate of supplementary bearing 3 alternately with suction chamber 11 in that the 8a of cylinder portion is inboard, the recess 23 that has microscler shape along Zhou Fangxiang in the 8a of cylinder portion is set.

The lubricant oil 16 that infeeds cylinder portion 8a inboard is supplied with recess 23.Then, to suction chamber 11 openings, the lubricant oil 16 of recess 23 is promptly supplied with suction chamber 11 as the front portion of recess 23.

As the anterior width b of recess 23 opening portions, be below the rotating speed of the specified running of hermetic type compressor low velocity zone, be stranded in below the oil slick thickness of the lubricant oil in the 8a of cylinder portion.Suitably set the angle [alpha] of width b, can the most suitably set the volume of recess 23 center of eccentric part 4a.

Because the width b of the opening portion of recess 23 is below the oil slick thickness of hermetic type compressor low velocity zone, so even such as the motor of compressor at low-speed running, also can cover recesses 23 by lubricant oil 16 comprehensively, improve the volumetric efficiency of the lubricant oil of absorption recess 23.Its result is even under the situation that oil mass changes in because of the rotation speed change cylinder 8a of portion, also can prevent in low velocity zone by the insufficient lubrication between the caused cylinder interior cold media air leakage current of the low on fuel in the cylinder 1 and slide member and cylinder hole portion.

In addition, owing to have with the rotation of compressor low velocity zone and coordinate mutually, revolution is drawn the open front portion of a certain amount of lubricant oil, and its front portion has become flow path resistance under the high velocity rotating speed, increases so can stop by the air-breathing loss on heating and the removal of lubricant amount that too much cause to oil mass that enter in the suction chamber.Thereby the closed type rotary compressor of use present embodiment is in the high reliability that can obtain under the wide range speed conditions under the high-performance.

Secondly, with Figure 12 fifth embodiment of the invention is described.In the present embodiment, the oil groove 21 that becomes store oil portion is located at that the 8a of cylinder portion is inboard to be to and from position on the end plate of supplementary bearing 3 alternately with suction chamber 11, eccentric part 4a is positioned at oil groove 21 front portions in supplementary bearing 3 sides with gap delta, has the place ahead supply unit that is made of eccentric part 4a and the 8a of cylinder portion.

The lubricant oil 16 of feed roller portion 8a inboard is communicated with the cylinder 8a of portion when inboard at oil groove 21, from the place ahead supply unit supply oil groove 21 that eccentric part 4a and the 8a of cylinder portion that leaves supplementary bearing 3 gap delta constitutes.Then, to suction chamber 11 openings, then the lubricant oil in the oil groove 21 16 is supplied with suction chamber 11 as oil groove 21.

The position of the face that faces toward supplementary bearing 3 of eccentric part 4a highly is positioned at oil groove 21 1 sides under the center line at eccentric part 4a mid-depth line facing to the 8a of cylinder portion, and for example, the gap delta that eccentric part 4a and supplementary bearing are 3 and the degree of depth h of oil groove 21 are about equally.

Because in cylinder portion 8a inboard, oil groove 21 side spatial volume diminish, the pasta of the lubricant oil of feed roller portion 8a inboard uprises at eccentric part 4a central direction, so even at the inboard lubricant oil 16 of only supplying with less oil groove 21 sides of the 8a of cylinder portion, lubricant oil 16 also can cover oil groove 21.Therefore, still can improve the volumetric efficiency of the lubricant oil of drawing oil groove 21.

Consequently, even under the situation that oil mass changes in the different cylinder 8a of portion because of rotating speed, revolution still can have a certain amount of lubricant oil to supply with suction chamber.That is, alleviated the low on fuel in the cylinder 1 of motor when low velocity zone turns round of hermetic type compressor, can prevent at the leakage current that is compressed cold media air of cylinder 1 inside and the insufficient lubrication between slide member and cylinder hole portion.In addition, also can prevent to enter when turning round by high velocity in the suction chamber to oil mass too much absorbing caused air-breathing loss on heating for anterior supply unit and be discharged in the suction chamber with pressing chamber in lubricants capacity increase.Thereby the closed type rotary compressor of use present embodiment can be in the high reliability that obtains under the speed conditions of wide range under the high-performance.

In above embodiment, employing in single cylinder type compressor, in the end face of supplementary bearing 3 form of oil groove 21, recess 22, recess 23 is set, but also can obtains same action effect naturally if be arranged on main bearing 2 both sides.The closed type rotary compressor that also can be used in addition, two cylinder type easily with structure with same configuration.

Bottom illustrates sixth embodiment of the invention with Figure 13.This kind circulation is freezing (air-cooling system) special-purpose circulation.Used the closed type rotary compressor 27 of one embodiment of the invention by starting, compressed High Temperature High Pressure start gas (cold media air) is pressed shown in the solid arrow, flow into condenser 24 from discharge tube 15, by the air-supply effect heat release liquefaction of condenser fan 24a.The refrigerant that this has liquefied is subjected to throttling in expansion valve 25, adiabatic expansion becomes low-temp low-pressure, become the liquid coolant of low-temp low-pressure, in the heat heat absorption of vaporizer 26, and after the gasification, suck closed type rotary compressors 27 through suction pipe 12 by the air of evaporator fan 26a supply.

Here, refrigeration system shown in Figure 13 owing to be to have carried the closed type rotary compressor that uses one embodiment of the invention, can obtain at the good refrigeration system of whole operating range effect.It is existing that details are as follows.

In Figure 13, speed control loop 50, the corresponding temperature that is detected by temperature transducer 51 decides the target temperature of refrigeration system, the rotational velocity of the motor that is had corresponding to its target temperature, control compressor 27.Be applied under the situation of refrigerating plants such as refrigerated warehouse at this refrigeration system, temperature transducer 51 be located at the place of the detected storehouse temperature of wanting detected temperatures.In addition, be used under the situation of air conditioners such as air compressor, be located at the next door that is assigned in indoor heat exchanger at this refrigeration system.Under the air conditioner situation, establish humidity transducer in the system, the rotating speed that the output value that speed control loop 50 is added humidity transducer is controlled motor also is effectively.Moreover, be used at this refrigeration system under the situation of hot water supply apparatus, establish and be used to measure through heat exchange, be heated the temperature transducer of the temperature of water.

Speed control loop 50 for control system reaches the target temperature of refrigeration system, the rotating speed of the motor with compressor 27 of control system.And controlling under the situation of compressor rotary speed for the effect of raising system, must guarantee that compressor efficient under different rotating speeds does not reduce.

To with the closed type rotary compressor 27 that uses embodiments of the invention refrigeration system as composed component, even changing the lubricant oil of feed roller portion inside, gives under the situation of oil mass the earthquake rotating speed, also often can supply with a certain amount of oil of suction chamber by revolution.

Reach under the condition of target temperature need not, need not to make motor (motor) high speed rotating of compressor, refrigeration system can be controlled compressor is slowly run.In this case, use the closed type rotary compressor of embodiments of the invention can not be created in low on fuel causes in the low velocity zone cylinder inside leakage current and the insufficient lubrication between slide member and cylinder hole portion.

In addition, reach at needs under the condition of target temperature, must make the motor high speed rotating of compressor, refrigeration system is controlled and is made compressor in high speed rotating.In this case, use the closed type rotary compressor of embodiments of the invention, can prevent from the air-breathing loss on heating that in the cylinder of high velocity, too much causes or discharge oil mass to increase to oil mass.

Particularly, in having used embodiments of the invention and closed type rotary compressor, owing to make seal container 6 internal pressures be lower than head pressure, thereby can reduce the amount in the High Temperature High Pressure refrigerant inflow evaporator when being interrupted running, can reduce the interruption energy loss.

Here very clear, even, embodiment is suitably revised, also be in example scope of the present invention according to refrigeration system or air-conditioning system needs.In addition, be illustrated, in compound compressor, also can use embodiments of the invention naturally using single stage compressor.Following one example.

Bottom illustrates seventh embodiment of the invention with Figure 14 and Figure 15.Here, to give and Fig. 1～Figure 13 in same symbol person, for identical parts plays same function.

In Figure 14 and Figure 15, compressing member 28 has low pressure compressing member 28a and high pressure compressing member 28b.The main bearing 30 and supplementary bearing 31 and dividing plate 32 of the axle supporting of double as live axle 29, the both ends open portion of stopping up the cylinder of each compressing member.The compressed action that shakes piston shape compressor of present embodiment, identical with Fig. 1 with situation of shaking piston shape compressor shown in Figure 3, but the mobile difference of cold media air.

Cold media air enters in the cylinder 1 ' of low pressure compressing member 28a and is compressed by the suction pipe 33 that is installed in seal container 6, the exhaust port 34a that compressed cold media air forms on main bearing 30 is discharged in the seal container 6 by exhaust silencer 35.

The cold media air that is discharged in the seal container 6 is discharged to the outside from discharge tube 36, after interstage cooler 37 heat releases cooling, enter the cylinder 1 of high pressure by suction pipe 38 with compressing member 28b " in; compressed cold media air enters by the tap hole 34b that is equipped on supplementary bearing 31 and discharges chamber 39, flows out to the outside by way of discharge tube 40 thus.

The oil supply mechanism of following explanation compression mechanical part.In Figure 14 and Figure 15,, making the blade part 8b of high pressure with compressing member 28b by the rotation of live axle 29 " advance and retreat are moved in the 1c of hole portion, change the volume of the 1c of hole portion.With the pumping action that this volume-variation was risen, store in the lubricant oil 16 of seal container 6 bottoms, attract by fluid one-way valve (ダ ィ ォ De) 41, by rail 19, on be drawn onto live axle 29, spiral goove 20 lubricated supplementary bearing 31, eccentric part 41a, 41b and main bearings 30 by being located at live axle 29 peripheries return in the seal container.

Lubricated the part of low pressure, supplied with suction chamber by the pressure reduction of the 8a ' of cylinder portion inner face and suction chamber with the lubricant oil 16 of the eccentric part 42a of compressing member 28a; Lubricated the part of high pressure, supplied with suction chamber with the main points identical with oil groove mode shown in Figure 4 with the lubricant oil 16 of the eccentric part 42b of compressing member 28b.

Here, oil groove is located at the either party of end face of end face, the dividing plate 32 of supplementary bearing 31, all can obtain effect same.

Cold media air by lubricant oil 16 foaming of passing through spiral goove 20, from gas fairlead 43a, 43b, drain to the 8a of cylinder portion by high pressure with the pressing chamber of compressing member 28b " high pressure refrigerant gas of inner face; by gas fairlead 43b;, be discharged to seal container 6 from being formed at the exhaust port 4c of live axle 29 inside.

Here, high pressure is with the 8a of cylinder portion of compressing member 28b " inner face; from pressing chamber 10 cold media air that bleeds and lubricant oil 16 coexistences of having lubricated eccentric part 42b; by the density difference of centrifugal force, lubricant oil and the cold media air of the rotation of live axle 29; because the high lubricant oil of density is positioned at the outside; low density cold media air is positioned at the inboard, only cold media air can be by the exhaust port 4c discharge that is formed at live axle 29 inside by gas fairlead 43b haply.In addition, on inner sealing, can not hinder the oil supply of oil groove, so can suppress inner leakage current to necessity of suction chamber.

As above, the horizontal piston type two stage compressor that shakes of present embodiment is owing to the oil groove 21 and notch part 8c that have as shown in Figure 4, so under the speed conditions of wide range, can guarantee high-performance and high reliability.

As detailed above, closed type rotary compressor of the present invention can be obtained high-performance and high reliability under the speed conditions of wide range.

Claims (10)

1. closed type rotary compressor, described compressor are provided with electric element with stator and rotor, transmit the rotation of this electric element and have the live axle of eccentric part and compressed by the rotation of this live axle eccentric part the compressing member of working fluid in seal container; It is characterized in that,

This compressing member is provided with: the cylinder with cylindric inner peripheral surface of both ends open, in this cylinder, be matched with the cylinder of aforementioned live axle eccentric part, follow the eccentric motion of aforementioned cylinder to be divided into the blade of suction chamber and pressing chamber in the aforementioned cylinder, the end plate of inaccessible cylinder opening, via aforementioned live axle lubricant oil is supplied to oil supply mechanism in the cylinder, has the portion that is taken into that is used for being taken into the lubricant oil that supplies to the cylinder inboard, with mutual connection at the space and the suction chamber of cylinder inboard and have lubricant oil feed mechanism to the holding part that keeps from the aforementioned lubricant oil that is taken into portion.

2. the closed type rotary compressor of recording and narrating by claim 1, it is characterized in that, the working fluid that it has aforementioned pressing chamber compression is discharged to the discharge tube of aforementioned seal container outside with running through aforementioned seal container, and makes the pressure ratio head pressure in the aforementioned seal container low.

3. the closed type rotary compressor of recording and narrating by claim 1 is characterized in that, the aforementioned portion of being taken into is a breach of being located at aforementioned cylinder end face; Aforementioned holding part is to be located at the recess of aforementioned end plate.

4. the closed type rotary compressor of recording and narrating by claim 1 is characterized in that, the aforementioned portion of being taken into is an annular ditch of being located at aforementioned cylinder end face; Aforementioned holding part is to be located at the recess of aforementioned end plate.

5. the closed type rotary compressor of recording and narrating by claim 1 is characterized in that, the aforementioned portion of being taken into is the space that is made of aforementioned cylinder portion, end plate and eccentric part; The rotor shaft direction center of the aforementioned relatively cylinder of the axial centre of aforementioned eccentric part is positioned at aforementioned holding part one side.

6. the closed type rotary compressor of recording and narrating by claim 5 is characterized in that, aforementioned holding part is to be located at the recess of aforementioned end plate; Aforementioned be taken into the aforementioned eccentric part of portion and be provided with the width in gap between the aforementioned end plate of aforementioned holding part and the recessed degree of depth of aforementioned holding part roughly the same.

7. the closed type rotary compressor of recording and narrating by claim 1 is characterized in that, the aforementioned portion of being taken into is the space that is made of aforementioned cylinder, end plate and eccentric part; Aforementioned holding part is to be located at the recess of aforementioned end plate, and described recess basal area on recessed depth direction changes.

8. the closed type rotary compressor of recording and narrating by claim 1 is characterized in that, the aforementioned portion of being taken into is the space that is made of aforementioned cylinder, end plate and eccentric part; Aforementioned holding part is to be located at the recess of aforementioned end plate, described recess with the perpendicular direction of recessed depth direction on basal area change.

9. the closed type rotary compressor of recording and narrating by claim 1 is characterized in that, the aforementioned portion of being taken into is along Zhou Fangxiang shaped aperture portion in the aforementioned cylinder; Aforementioned holding part is to be located at the recess of aforementioned end plate.

10. refrigeration system, described refrigeration system has: compress the closed type rotary type compression of the working fluid that sucks by suction pipe with the driving force of motor, be taken into and condenser condensing by the working fluid of discharge tube compression, make expansion mechanism through the working fluid adiabatic expansion of this condenser condenses, be taken into the vaporizer of working fluid from this expansion mechanism, based on the information of sensor decision target temperature and to should target temperature controlling the speed control loop of the motor rotational velocity of aforementioned closed type rotary compressor, it is characterized in that

Aforementioned closed type rotary compressor, in seal container, have: be provided with based on the control of aforementioned speed control loop change the motor of rotational velocity electric element, have the live axle that transmits the eccentric part that the aforementioned electric motivation rotates and by the compressing member of the rotation compression working fluid of the eccentric part of this live axle;

Described compressing member is provided with: the cylinder with cylindrical shape inner peripheral surface of both ends open, in this cylinder, be matched with the cylinder of the eccentric part of aforementioned live axle, follow the eccentric motion of this cylinder to be divided into the blade of suction chamber and pressing chamber in the aforementioned cylinder, the end plate of inaccessible cylinder opening, oil supply mechanism via supplying lubricating oil in the aforementioned driving axial cylinder, has the portion that is taken into that is used for being taken into to the inboard lubricant oil of supplying with of cylinder, with mutual connection at cylinder inner space and suction chamber and have lubricant oil feed mechanism to the holding part that keeps from the aforementioned lubricant oil that is taken into portion.

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