CN101655091A - Rotary compressor - Google Patents

Abstract

The invention discloses a rotary compressor. In a compression mechanism (30) of a rotary compressor, cylinder chambers (60, 65) are formed by a cylinder (40) and a second housing (50). A back side space (75) is formed between an end plate (41) of the cylinder (40) and a flat plate section (36) of a first housing (35). A communication path (81) and a differential pressure valve (82) are arranged inthe first housing (35). When the difference between a discharge pressure and a suction pressure is small, the discharge pressure is introduced into an intermediate space (77) through the communication path (81), which causes both an inner space (76) and the intermediate space (77) to be at the discharge pressure. As a result, pressing force acting on the cylinder (40) is greater. On the contrary,when the difference between the discharge pressure and the suction pressure is large, the communication path (81) is blocked by the differential pressure valve (82), which causes the pressure in theintermediate space (77) to be at an intermediate pressure lower than the discharge pressure. As a result, pressing force acting on the cylinder (40) is smaller.

Description

Rotary compressor

The application is to be on May 23rd, 2006, denomination of invention to be the dividing an application of Chinese invention patent application of 200680013669.8 (PCT/JP2006/310235) for " rotary compressor ", application number the applying date.

Technical field

[0001] the present invention relates to a kind of by allowing cylinder and piston relatively carry out the rotary compressor that eccentric rotation comes compressed fluid.

Background technique

[0002] up to now, for example, the rotary compressor quilt that is disclosed in the patent documentation 1 is well-known.This rotary compressor comprises the piston element of cylinder and eccentric rotation.Cylinder and piston element become the compressor of enclosed space.And, in each of cylinder and piston element, be formed with end wall.It is relative that the end wall of cylinder and the end wall of piston element clip pressing chamber.And this rotary compressor compresses the fluid that is drawn into pressing chamber by allowing piston element carry out the off-centre rotation.

[0003] in this rotary compressor, the interior pressure of pressing chamber acts on each end wall in the end wall of the end wall of cylinder and piston element.When the fluid in the pressing chamber is compressed, press liter in the pressing chamber.Therefore, if do not take any countermeasure, cylinder and piston element can move because of the opposite towards each other direction of pressure that acts on the end wall separately, and the result causes the sealing state that can not fully keep pressing chamber, causes the decline of compression efficiency.

[0004] so, in the rotary compressor shown in the above-mentioned patent documentation 1, allow pushing force act on the end wall of piston element, prevent the phenomenon of the gap enlargement between piston element and the cylinder, guarantee the sealing state of pressing chamber.

Patent documentation 1: the spy opens flat 6-288358 communique

[0005] above-mentioned rotary compressor sucks the fluid of low pressure, compresses, and becomes the fluid of high pressure after ejection is compressed.According to the purposes difference of this rotary compressor, suck sometimes cylinder chamber the suction fluid pressure and can produce change from the pressure of the ejecting fluid of cylinder chamber ejection.For example, when this rotary compressor was used as the compressor of the air conditioner that carries out refrigeration cycle, the pressure that sucks fluid and ejecting fluid can change because of the operating condition of air conditioner.

[0006] when the pressure that sucks fluid and ejecting fluid changes, should allow the size that acts on the pushing force on the piston element also can change thereupon.Therefore, in the rotary compressor of above-mentioned patent documentation 1, sometimes because of its operating condition makes the pushing force surplus that acts on the piston element, at this moment, the friction between piston element and the cylinder can become greatly, might cause the increase of mechanical loss.

Summary of the invention

[0007] the present invention is the invention in view of the premises, and purpose is: even when the operating condition of rotary compressor changes, also can guarantee higher compression efficiency under the situation that does not increase mechanical loss.

[0008] first invention is that with such rotary compressor be object, comprise the cylinder 40 that forms cylinder chamber 60,65, with the state with respect to these cylinder 40 off-centre be accommodated in the said cylinder chamber 60,65 piston 50 and in order to said cylinder chamber 60,65 is divided into the blade 45 of hyperbaric chamber 61,66 and low pressure chamber 62,67.This rotary compressor relatively carries out the off-centre rotation by said cylinder 40 and above-mentioned piston 50, and the volume of above-mentioned hyperbaric chamber 61,66 and low pressure chamber 62,67 is changed.And, being respectively arranged with runner plate portion at the terminal side of said cylinder 40 and the terminal side of above-mentioned piston 50, it is relative that runner plate portion 51 front surface separately of the runner plate portion 41 of said cylinder 40 and above-mentioned piston 50 clips said cylinder chamber 60,65.One of them formation in said cylinder 40 and the above-mentioned piston 50 pushes away side component, and another formation is accepted side component.This rotary compressor comprises: pushing and pressing mechanism 70 pushes the above-mentioned side component that pushes away towards the above-mentioned runner plate portion that accepts side component; And controlling mechanism 80, according to the suction fluid that is inhaled into above-mentioned low pressure chamber 62,67 and from above-mentioned hyperbaric chamber the pressure difference of the ejecting fluid of 61,66 ejections, change and act on the above-mentioned size that pushes away on the side component towards the load of the above-mentioned runner plate portion direction of accepting side component.

[0009] in first invention, is isolated into hyperbaric chamber 61,66 and low pressure chamber 62,67 by blade 45 by the cylinder chamber 60,65 of cylinder 40 and piston 50 encirclements.When cylinder 40 and piston 50 relatively carried out the off-centre rotation, the volume of hyperbaric chamber 61,66 and low pressure chamber 62,67 changed.In the process that the volume of low pressure chamber 62,67 enlarges, fluid is inhaled into low pressure chamber 62,67, and in the process that the volume in hyperbaric chamber 61,66 dwindles, the fluids in the hyperbaric chamber 61,66 are compressed.Hydrodynamic pressure in the hyperbaric chamber 61,66 is with respect to each effect in the runner plate portion 51 of the runner plate portion 41 of cylinder 40 and piston 50, the direction that both are left toward each other.

[0010] on the other hand, be provided with pushing and pressing mechanism 70 at rotary compressor 10 of the present invention.Pushing and pressing mechanism 70 acts on pushing force in cylinder 40 and the piston 50 any one.In the present invention, make in cylinder 40 and the piston 50, accept pushing force from pushing and pressing mechanism 70 one for pushing away side component, remaining one for accepting side component.When cylinder 40 for pushing away side component, piston 50 allows pushing and pressing mechanism 70 with respect to for pushing away the cylinder 40 of side component when accepting side component, effect is oriented the pushing force of runner plate portion 51 directions of the piston 50 of accepting side component.On the contrary, when piston 50 for pushing away side component, cylinder 40 allows pushing and pressing mechanism 70 with respect to for pushing away the piston 50 of side component when accepting side component, effect is oriented the pushing force of runner plate portion 41 directions of the cylinder 40 of accepting side component.The pushing force of this pushing and pressing mechanism 70 makes in cylinder 40 and the piston 50 one of them be pushed to another runner plate portion.

[0011] here, in comprising the rotary compressor in the past 10 that only is equivalent to this pushing and pressing mechanism 70, act in the load that pushes away on the side component, become power that the runner plate portion that pushes away side component accepts from the fluid in the hyperbaric chamber 61,66 and the making a concerted effort of the power accepted from pushing and pressing mechanism 70 towards the size of the load of the runner plate portion direction of accepting side component.And, when comparing, push away power that side component accepts from pushing and pressing mechanism 70 when excessive with the power that fluid in hyperbaric chamber 61,66 is accepted, act on the frictional force that pushes away side component and accept between the side component and become big, cause that power loss (that is frictional loss) increases.

[0012] so, in the present invention, be provided with controlling mechanism 80 at rotary compressor 10.This controlling mechanism 80 in order in the load of regulating action on pushing away side component, towards the size of the load of the runner plate portion direction of accepting side component.At that time, controlling mechanism 80 is according to the pressure (that is suction pressure) of the suction fluid that sucks low pressure chamber 62,67 and the difference of the pressure (that is ejection pressure) of the ejecting fluid of 61,66 ejections is regulated this load from the hyperbaric chamber size.

[0013] second invention is on the basis of first invention, the cross section that said cylinder 40 constitutes said cylinder chamber 60,65 is a ring-type, above-mentioned piston 50 comprises piston only 52, this piston only 52 forms ring-type, and said cylinder chamber 60,65 is divided into the outside cylinder chamber 60 in these piston 50 outsides and the inboard cylinder chamber 65 of this piston 50 inboards.Each cylinder chamber in above-mentioned outside cylinder chamber 60 and the inboard cylinder chamber 65 is divided into hyperbaric chamber 61,66 and low pressure chamber 62,67 by above-mentioned blade 45.

[0014] in second invention, the cross section of the cylinder chamber 60,65 that is formed by cylinder 40 cross section of the axle direction quadrature of cylinder 40 (that is, with) becomes ring-type.This cylinder chamber 60,65 is isolated into outside cylinder chamber 60 and inboard cylinder chamber 65 by annular piston 50.The outside cylinder chamber 60 that is positioned at piston 50 outsides is isolated into hyperbaric chamber 61 and low pressure chamber 62 by blade 45.And the inboard cylinder chamber 65 that is positioned at piston 50 inboards also is isolated into hyperbaric chamber 66 and low pressure chamber 67 by blade 45.When piston 50 and cylinder 40 relatively carried out the off-centre rotation, the volume of these hyperbaric chambers 61,66 and low pressure chamber 62,67 changed, and carried out towards the suction of the fluid of low pressure chamber 62,67 and the compression of the fluid in hyperbaric chamber 61,66.

[0015] the 3rd invention is on the basis of above-mentioned first or second invention, above-mentioned controlling mechanism 80 allows above-mentioned pushing and pressing mechanism 70 towards the above-mentioned size that pushes away the pushing force of side component effect by change, changes to act on the above-mentioned size towards the load of the above-mentioned runner plate portion direction of accepting side component that pushes away on the side component.

[0016] in the 3rd invention, controlling mechanism 80 changes push away the size of side component from the pushing force of pushing and pressing mechanism 70 acceptance itself.And, after controlling mechanism 80 changes the size of pushing force of pushing and pressing mechanism 70, act on the size that pushes away on the side component and change towards the load of the runner plate portion that accepts side component.

[0017] the 4th invention is on the basis of above-mentioned the 3rd invention, above-mentioned pushing and pressing mechanism 70 constitutes and allows the pressure of above-mentioned ejecting fluid act on the part at the above-mentioned runner plate portion back side that pushes away side component, allows the pressure of above-mentioned suction fluid act on the rest parts.The area of the part of above-mentioned controlling mechanism 80 by changing pressure effect in the above-mentioned runner plate portion back side that pushes away side component, above-mentioned ejecting fluid changes and allows above-mentioned pushing and pressing mechanism 70 towards the above-mentioned size that pushes away the pushing force of side component effect.

[0018] in the 4th invention, pushing and pressing mechanism 70 allows pushing force act on and pushes away on the side component by allowing the pressure of ejecting fluid and suction fluid act on the runner plate portion back side that pushes away side component.And controlling mechanism 80 changes the area of the part of pressure in the runner plate portion back side that pushes away side component, that accept ejecting fluid.If the situation identical to the pressure of ejecting fluid compares, the area of part that then pushes away pressure in the runner plate portion back side of side component, that accept ejecting fluid is wide more, and it is big more to act on the pushing force that pushes away on the side component.

[0019] the 5th invention is on the basis of above-mentioned the 4th invention, is provided with supporting part 35, and this supporting part 35 is along the above-mentioned runner plate portion back side configuration that pushes away side component, and the whole back side of this runner plate portion between form back side gap 75.Above-mentioned pushing and pressing mechanism 70 comprises and forms ring-type and major diameter seal ring 71 that is configured in above-mentioned back side gap 75 and the minor diameter seal ring 72 that diameter differs from one another, allow the pressure of above-mentioned ejecting fluid constantly act on the part of above-mentioned minor diameter seal ring 72 inboards in the above-mentioned back side gap 75, allow the pressure of above-mentioned suction fluid constantly act on the part in above-mentioned major diameter seal ring 71 outsides.Above-mentioned controlling mechanism 80 comprises access 81 and open and close valve 82, this access 81 is connected to the space that above-mentioned ejecting fluid exists with part in the above-mentioned back side gap 75, between above-mentioned minor diameter seal ring 72 and the major diameter seal ring 71, when this open and close valve 82 is lower than specified value in the pressure difference of above-mentioned ejecting fluid and above-mentioned suction fluid, open above-mentioned access 81, become specified value when above in this pressure difference, close above-mentioned access 81.

[0020] in the 5th invention, supporting part 35 with push away formation back side gap 75 between the runner plate portion of side component.This back side gap 75 is isolated into 3 parts by major diameter seal ring 71 and minor diameter seal ring 72.Specifically, back side gap 75 is divided into the part between inside part, minor diameter seal ring 72 and the major diameter seal ring 71 of minor diameter seal ring 72 and the external lateral portion of major diameter seal ring 71.In the side clearance 75, the inside part of minor diameter seal ring 72 and the pressure of ejecting fluid are roughly the same overleaf, and the external lateral portion of major diameter seal ring 71 is roughly the same with the pressure that sucks fluid.

[0021] in the present invention, be provided with access 81 and open and close valve 82 at controlling mechanism 80.

[0022] pressure difference at ejecting fluid and suction fluid is lower than under the state of specified value, and open and close valve 82 is opened access 81.Under this state, the pressure of ejecting fluid is imported into part in the back side gap 75, between minor diameter seal ring 72 and the major diameter seal ring 71.That is to say that in the side clearance 75, the whole inboard of major diameter seal ring 71 becomes the pressure of ejecting fluid overleaf, only have the outside of major diameter seal ring 71 to become the pressure that sucks fluid.Be fixed up if will push away the area of the part of pressure effect in the runner plate portion of side component, that allow ejecting fluid, then might and suck under the less state of the pressure difference of fluid, act on the pushing force that pushes away on the side component and can produce deficiency in ejecting fluid.So it is ejecting fluid that controlling mechanism 80 makes the whole inboard of the major diameter seal ring 71 in the back side gap 75, guarantees to act on the pushing force that pushes away on the side component.

[0023] opposite, under ejecting fluid and the pressure difference that sucks fluid became state more than the specified value, open and close valve 82 was closed access 81.Under this state, minor diameter seal ring 72 in the back side gap 75 and the part between the major diameter seal ring 71 are the pressure of ejecting fluid and the intermediate value that sucks the pressure of fluid.That is to say, because major diameter seal ring 71 and minor diameter seal ring 72 are not to have stoped spilling of fluid fully, therefore overleaf in the side clearance 75, the pressure between minor diameter seal ring 72 and the major diameter seal ring 71 becomes the intermediate value of the pressure in the pressure of minor diameter seal ring 72 inboards and major diameter seal ring 71 outsides.When allowing the area of part of pressure effect of ejecting fluid be fixed up in the runner plate portion that pushes away side component, in ejecting fluid with suck under the bigger state of the pressure difference of fluid, acting on the pushing force that pushes away on the side component might be superfluous.So controlling mechanism 80 makes the pressure of minor diameter seal ring 72 in the back side gap 75 and the part between the major diameter seal ring 71 be lower than the pressure of ejecting fluid, cuts down and acts on the pushing force that pushes away on the side component.

[0024] the 6th invention is on the basis of above-mentioned first or second invention, is provided with supporting part 35, and this supporting part 35 is along the above-mentioned runner plate portion back side configuration that pushes away side component, and the whole back side of this runner plate portion between form back side gap 75.Above-mentioned pushing and pressing mechanism 70 constitute hydrodynamic pressure by above-mentioned back side gap 75 with the above-mentioned side component that pushes away towards the above-mentioned runner plate portion pushing of accepting side component, and dispose major diameter seal ring 71 and the minor diameter seal ring 72 that forms the ring-type that diameter differs from one another in above-mentioned back side gap 75.Above-mentioned controlling mechanism 80 allows above-mentioned pushing and pressing mechanism 70 change towards the above-mentioned size that pushes away the pushing force of side component effect by changing the hydrodynamic pressure of part in the above-mentioned back side gap 75, between above-mentioned minor diameter seal ring 72 and the major diameter seal ring 71.

[0025] in the 6th invention, between runner plate portion that pushes away side component and supporting part 35, forms back side gap 75.Pushing and pressing mechanism 70 allows pushing force act on and pushes away on the side component by allowing the fluid pressure action that is present in back side gap 75 at the runner plate portion back side that pushes away side component.On the other hand, controlling mechanism 80 constitutes the above-mentioned minor diameter seal ring 72 that can regulate in the above-mentioned back side gap 75 and the hydrodynamic pressure of the part between the major diameter seal ring 71.When the hydrodynamic pressure of this part changes, push away the side component power that the fluids in 75 are accepted from the back side gap and change, the result makes and acts on the size towards the load of the above-mentioned runner plate portion direction of accepting side component that pushes away on the side component and change.

[0026] the 7th invention is on the basis of above-mentioned the 6th invention, being centered close to than the rotating center of said cylinder 40 or above-mentioned piston 50 position near above-mentioned hyperbaric chamber 61,66 of above-mentioned major diameter seal ring 71.

[0027] in the 7th invention, major diameter seal ring 71 is configured to its deflection hyperbaric chamber, central position 61,66 sides.Here, the hydrodynamic pressure that acts in the runner plate portion of piston 50 and cylinder 40 is that hyperbaric chamber 61,66 sides are greater than low pressure chamber 62,67 sides.Therefore, only allow pushing force act on fifty-fifty in the runner plate portion that pushes away side component for piston 50 or cylinder 40, the moment that allows piston 50 and cylinder 40 tilt is stayed.And if major diameter seal ring 71 is configured in locational words near hyperbaric chamber 61,66, the interior pressure of part in the back side gap 75, that clipped by minor diameter seal ring 72 and major diameter seal ring 71 then can make the point of action that acts on the pushing force in the runner plate portion that pushes away side component become position near hyperbaric chamber 61,66.So, reduced to allow pushing away the moment that side component tilts.

[0028] the 8th invention is on the basis of above-mentioned the 5th invention, above-mentioned major diameter seal ring 71 and above-mentioned minor diameter seal ring 72 being centered close to separately, and being centered close to of above-mentioned minor diameter seal ring 72 than position, the center of above-mentioned major diameter seal ring 71 near above-mentioned blade 45 than the rotating center of said cylinder 40 or above-mentioned piston 50 position near above-mentioned hyperbaric chamber 61,66.

[0029] in the 8th invention, major diameter seal ring 71 and minor diameter seal ring 72 central position separately are configured to be partial to hyperbaric chamber 61,66 sides.Here, the hydrodynamic pressure that acts in the runner plate portion of piston 50 and cylinder 40 is that hyperbaric chamber 61,66 sides are greater than low pressure chamber 62,67 sides.Therefore, if only allow pushing force act on the runner plate portion that pushes away side component fifty-fifty, the moment that allows piston 50 and cylinder 40 tilt is stayed for piston 50 or cylinder 40.And if major diameter seal ring 71 and minor diameter seal ring 72 are configured to then pushing away the runner plate portion of side component near hyperbaric chamber 61,66, the pushing force that acts on the part in hyperbaric chamber 61,66 is compared with the part near low pressure chamber 62,67, and is bigger.So, reduced to allow pushing away the moment that side component tilts.

[0030] and, in the present invention, the eccentric direction of major diameter seal ring 71 is different with the eccentric direction of minor diameter seal ring 72.Therefore, only have the inboard of minor diameter seal ring 72 to become under the pressure status of ejecting fluid overleaf in the side clearance 75 and the whole inboard of major diameter seal ring 71 becomes under the pressure status of ejecting fluid, the position that acts on the action center of the pushing force in the runner plate portion that pushes away side component changes.That is to say that the position that the pressure official post of ejecting fluid and suction fluid acts on the action center of the pushing force in the runner plate portion that pushes away side component changes.

[0031] the 9th invention is on the basis of above-mentioned first or second invention, above-mentioned controlling mechanism 80 acts on the above-mentioned size towards the load of the above-mentioned runner plate portion direction of accepting side component that pushes away on the side component and changes by allowing the masterpiece that pushes back of the direction left from the above-mentioned runner plate portion that accepts side component be used in and above-mentionedly push away on the side component and change the size that this pushes back power, allowing.

[0032] in the 9th invention, controlling mechanism 80 transference towards pushing away the side component effect, changes the size that this pushes back power from the opposite power that pushes back of the pushing force direction of pushing and pressing mechanism 70.Owing to cancel out each other with the power that pushes back of controlling mechanism 80, therefore when controlling mechanism 80 changes push back power big or small, act on the size that pushes away on the side component and change towards the load of the runner plate portion that accepts side component by the pushing force that pushing and pressing mechanism 70 produces.

[0033] the tenth invention is on the basis of above-mentioned the 9th invention, above-mentioned controlling mechanism 80 is included in the above-mentioned groove 88 of accepting the front-end face opening of side component with the front surface sliding contact of the above-mentioned runner plate portion that pushes away side component, by changing the interior pressure of this groove 88, change the size of the above-mentioned power of pushing back.

[0034] in the tenth invention, groove 88 is being accepted the front-end face opening of side component.The interior pressure of this groove 88 acts on the front surface of the runner plate portion that pushes away side component.That is to say that the interior pressure of groove 88 makes and acts on the direction that pushes away the power on the side component and become and make the runner plate portion that pushes away side component from accepting the direction that side component leaves.Controlling mechanism 80 is by changing the interior pressure of groove 88, allows size variation towards the power that pushes back that pushes away the side component effect.

[0035] the 11 invention is on the basis of above-mentioned the tenth invention, the groove 88 of above-mentioned controlling mechanism 80 in the above-mentioned front-end face of accepting side component near the part opening of above-mentioned low pressure chamber 62,67.Above-mentioned controlling mechanism 80 comprises access 81 and open and close valve 82, this access 81 is connected to the space that above-mentioned ejecting fluid exists with above-mentioned groove 88, when this open and close valve 82 surpasses specified value in the pressure difference of above-mentioned ejecting fluid and above-mentioned suction fluid, open above-mentioned access 81, become specified value when following in this pressure difference, close above-mentioned access 81.

[0036] in the 11 invention, the part opening of the close low pressure chamber 62,67 of groove 88 in accepting the front-end face of side component.Under ejecting fluid and the pressure difference that sucks fluid become state more than the specified value, open access 81 by open and close valve 82.Under this state, the pressure of ejecting fluid is imported into groove 88 by access 81.In ejecting fluid with suck under the bigger state of the pressure difference of fluid, set the interior pressure of groove 88 pressure of ejecting fluid for, increase the push back power opposite with the pushing force direction of pushing and pressing mechanism 70.On the contrary, be lower than under the state of specified value, close access 81 by open and close valve 82 in ejecting fluid and the pressure difference that sucks fluid.Under this state, be subjected in the low pressure chamber 62,67 and the influence of the hydrodynamic pressure in the hyperbaric chamber 61,66, the interior pressure of groove 88 becomes and is lower than the pressure of ejecting fluid.In ejecting fluid with suck under the less state of the pressure difference of fluid, make groove 88 in force down pressure in ejecting fluid, reduce the push back power opposite with the pushing force direction of pushing and pressing mechanism 70.

[0037] as mentioned above, act on for the hydrodynamic pressure on the front surface of the runner plate portion that pushes away side component of piston 50 or cylinder 40 be that low pressure chamber 62,67 sides are less than hyperbaric chamber 61,66 sides.And in the present invention, in accepting the front-end face of side component near allowing groove 88 openings in the part of low pressure chamber 62,67.And when by access 81 pressure of ejecting fluid being led this groove 88, the power that pushes back that acts on the part of low pressure chamber 62,67 sides in the runner plate portion that pushes away side component becomes big, allows push away the moment that side component tilts and diminish.

[0038] the 12 invention is on the basis of above-mentioned the tenth invention, the groove 88 of above-mentioned controlling mechanism 80 in the above-mentioned front-end face of accepting side component near the part opening in above-mentioned hyperbaric chamber 61,66.Above-mentioned controlling mechanism 80 comprises access 81 and open and close valve 82, this access 81 is connected to the space that above-mentioned suction fluid exists with above-mentioned groove 88, when this open and close valve 82 is lower than specified value in the pressure difference of above-mentioned ejecting fluid and above-mentioned suction fluid, open above-mentioned access 81, become specified value when above in this pressure difference, close above-mentioned access 81.

[0039] in the 12 invention, the part opening in groove 88 close hyperbaric chamber 61,66 in accepting the front-end face of side component.Under ejecting fluid and the pressure difference that sucks fluid become state below the specified value, utilize open and close valve 82 to open access 81.Under this state, the pressure that sucks fluid is imported into groove 88 by access 81.Under the less state of the pressure difference of ejecting fluid and suction fluid, set the interior pressure of groove 88 for suck fluid pressure, reduce the push back power opposite with the pushing force direction of pushing and pressing mechanism 70.On the contrary, surpass under the state of specified value, utilize open and close valve 82 to close access 81 in ejecting fluid and the pressure difference that sucks fluid.Under this state since in hyperbaric chamber 61,66 the compressed fluid groove 88 that only a little bleeds, so the interior pressure of groove 88 becomes and is higher than the pressure that sucks fluid.In ejecting fluid with suck under the bigger state of the pressure difference of fluid, make the interior pressure of groove 88 be higher than the pressure of ejecting fluid, increase the push back power opposite with the pushing force direction of pushing and pressing mechanism 70.

[0040] as mentioned above, act on for the hydrodynamic pressure on the front surface of the runner plate portion that pushes away side component of piston 50 or cylinder 40 be that hyperbaric chamber 61,66 sides are greater than low pressure chamber 62,67 sides.And in the present invention, in accepting the front-end face of side component near allowing groove 88 openings in the part in hyperbaric chamber 61,66.And, when the pressure that will suck fluid by access 81 imports this groove 88, act on the part of hyperbaric chamber 61,66 sides in the runner plate portion that pushes away side component to push back power less, allow to push away the moment that side component tilts less.

(effect of invention)

[0041] in the present invention, pushing and pressing mechanism 70 allows pushing force act on to be one of them push away on the side component in cylinder 40 or the piston 50.Therefore, though the fluid pressure action in the cylinder chamber 60,65 in the runner plate portion of cylinder 40 and piston 50, also can be not under the condition of enlarged in the gap of cylinder 40 and piston 50, suppression fluid 61,66 spills from the hyperbaric chamber, improves compression efficiency.And in the present invention, acting on the size that pushes away the load on the side component is to be regulated according to the difference of ejection pressure and suction pressure by controlling mechanism 80.Therefore, even when the operating condition of rotary compressor 10 changes, also can suitably set act in the load that pushes away on the side component, towards the size of the load of the runner plate direction of accepting side component, can reduce by pushing away side component and accepting the loss that friction caused between the side component.So, according to the present invention, can improve the compression efficiency of rotary compressor 10, simultaneously, reduce the mechanical loss in this running, can seek to improve the performance of rotary compressor 10.

[0042] and, according to above-mentioned the 3rd～the 8th invention because controlling mechanism 80 is regulated the size of the pushing force self that is produced by pushing and pressing mechanism 70, therefore exactly regulating action in the size that pushes away the load on the side component.Particularly according to above-mentioned the 7th, the 8th invention, even the operating condition of rotary compressor 10 changes, the pressure difference of ejecting fluid and suction fluid changes, also can positively cut down one of them the size that pushes away the moment that side component tilts that allows in cylinder 40 and the piston 50, can avoid because of problems such as the reduction that pushes away the compression efficiency that the side component inclination causes and eccentric wear damages.

[0043] and, according to above-mentioned the 9th～the 12 invention because controlling mechanism 80 is regulated the size of the push back power opposite with the pushing force direction that is produced by pushing and pressing mechanism 70, so exactly regulating action in the size that pushes away the load on the side component.Particularly according to the 11 and the 12 invention, can reduce allowing the size that pushes away the moment that side component tilts, can avoid because of problems such as the reduction that pushes away the compression efficiency that the side component inclination causes and eccentric wear damages.

Description of drawings

[0044] Fig. 1 is the summary longitudinal sectional drawing of first embodiment's rotary compressor.

Fig. 2 is the transverse cross-sectional view of wanting portion of expression first embodiment's compressing mechanism.

Fig. 3 is the longitudinal sectional drawing of wanting portion of expression first embodiment's compressing mechanism, and Fig. 3 (A) is in the figure of open mode for representing access, and Fig. 3 (B) is in the figure of closed condition for the expression access.

Fig. 4 is the transverse cross-sectional view of wanting portion of expression first embodiment's compressing mechanism.

Fig. 5 is the transverse cross-sectional view of the compressing mechanism of the action of expression rotary compressor.

Fig. 6 is the longitudinal sectional drawing of wanting portion of expression second embodiment's compressing mechanism.

Fig. 7 is the transverse cross-sectional view of wanting portion of expression second embodiment's compressing mechanism.

Fig. 8 is the longitudinal sectional drawing of wanting portion of expression the 3rd embodiment's compressing mechanism.

Fig. 9 is the transverse cross-sectional view of wanting portion of expression the 3rd embodiment's compressing mechanism.

Figure 10 is the transverse cross-sectional view of wanting portion of the compressing mechanism in other embodiment's of expression first variation.

Figure 11 is the summary longitudinal sectional drawing of the rotary compressor in other embodiment's second variation.

Figure 12 is the summary longitudinal sectional drawing of the rotary compressor in other embodiment's the 3rd variation.

(explanation of symbol)

[0045] 10-rotary compressor; 35-first shell (supporting part); The 40-cylinder; 41-runner plate portion; The 45-blade; 50-second shell (piston); 51-runner plate portion; The 52-piston only; 60-outside cylinder chamber; The 61-hyperbaric chamber; The 62-low pressure chamber; The inboard cylinder chamber of 65-; The 66-hyperbaric chamber; The 67-low pressure chamber; The 70-pushing and pressing mechanism; 71-major diameter seal ring; 72-minor diameter seal ring; 75-back side gap; The 80-controlling mechanism; The 81-access; 82-defferential valve (open and close valve); The 88-groove.

Embodiment

[0046] below, embodiments of the invention is described in detail with reference to accompanying drawing.

[0047] (first embodiment)

Embodiments of the invention are illustrated.The rotary compressor 10 of present embodiment is set in the refrigerant circuit of refrigerating machine, is used for compressed refrigerant.

[0048] as shown in Figure 1, the rotary compressor 10 of present embodiment constitutes so-called full enclosed type.This rotary compressor 10 has the housing 11 that forms lengthwise seal container shape.This housing 11 is made of cylindrical part 12 and pair of end board 13, and it is cylindric that this cylindrical part 12 forms lengthwise, and this pair of end board 13 forms bowl-shape, and the two ends of cylindrical part 12 are blocked.Be provided with the spraying pipe 14 of this end plate portion 13 of perforation at upside board 13.Be provided with the suction pipe 15 that connects this cylindrical part 12 in cylindrical part 12.

[0049] disposes compressing mechanism 30 and motor 20 from bottom to top successively in the inside of housing 11.And, be provided with the crankshaft 25 that extends at above-below direction in the inside of housing 11.Compressing mechanism 30 and motor 20 link together by crankshaft 25.The rotary compressor 10 of present embodiment is so-called high-pressure dome type.That is to say that refrigerant compressed is sprayed to the inner space of housing 11 in compressing mechanism 30, then, send from housing 11 by spraying pipe 14.

[0050] crankshaft 25 comprises main shaft part 26 and eccentric part 27.Eccentric part 27 is set on the position of close lower end of crankshaft 25, forms diameter cylindric greater than main shaft part 26.The axle center of this eccentric part 27 is from the only eccentric amount of stipulating in the axle center of main shaft part 26.The inside of crankshaft 25 be formed with from the lower end of crankshaft 25 towards above the fuel feeding path that extends, do not have diagram.The underpart of this fuel feeding path constitutes so-called centrifugal pump.The lubricant oil that amasss in housing 11 bottoms is provided for compressing mechanism 30 by this fuel feeding path.

[0051] motor 20 comprises stator 21 and rotor 22.Stator 21 is fixed on the inwall of the cylindrical part 12 of housing 11.Rotor 22 is configured in the inboard of stator 21, links together with the main shaft part 26 of crankshaft 25.

[0052] compressing mechanism 30 comprises first shell 35, second shell 50 and cylinder 40.In this compressing mechanism 30, first shell 35 and second shell 50 are being provided with the relation of upper-lower position, have taken in cylinder 40 in by the space of first shell 35 and 50 encirclements of second shell.

[0053] first shell 35 comprises plat part 36, peripheral portion 38 and bearing portion 37, constitutes supporting part.Plat part 36 forms thicker discoideus, and the internal diameter of its external diameter and housing 11 is almost equal.This plat part 36 is fixed on the cylindrical part 12 of housing 11 by methods such as weldings.And the main shaft part 26 of crankshaft 25 connects the middle body of plat part 36.Peripheral portion 38 forms near the cylindric of continuous weak point the periphery of plat part 36, gives prominence to being provided with towards the below from the front surface (lower surface Fig. 1) of plat part 36.Be formed with the suction passage (port) 39 that connects this peripheral portion 38 towards diametric(al) at peripheral portion 38, suction pipe 15 inserts in this suction passage 39.Bearing portion 37 form along main shaft part 26 extend cylindric, from the back side (upper surface Fig. 1) of plat part 36 towards the top outstanding the setting.This bearing portion 37 constitutes the sliding bearing of supports main shaft portion 26.

[0054] second shell 50 comprises runner plate portion 51 and piston only 52, constitutes piston.Runner plate portion 51 forms thicker discoideus, and its external diameter is slightly smaller than the internal diameter of housing 11.This runner plate portion 51 is connected on first shell 35 by bolt etc., and the peripheral portion 38 of first shell 35 withstands on its front surface (upper surface among Fig. 1).And the main shaft part 26 of crankshaft 25 connects the middle body of runner plate portion 51, and this runner plate portion 51 constitutes the sliding bearing of supports main shaft portion 26.Piston only 52 forms as one with runner plate portion 51, and is outstanding from the front surface of runner plate portion 51.This piston only 52 is to be seen as " C " font from the plane than the shape after the part excision of short cylinder.Again the details of piston only 52 is illustrated later on.

[0055] cylinder 40 comprises runner plate portion 41, outside cylinder part 42 and inboard cylinder part 43, is configured in the space of peripheral portion 38 inboards that are formed on first shell 35.Between the outer circumferential face of the inner peripheral surface of this peripheral portion 38 and cylinder 40, be formed with the space.This space is communicated with suction passage 39, constitutes to suck space 57.

[0056] runner plate portion 41 is the ring-like of diametric wider width, forms thicker planar.Runner plate portion 41 is that the lower surface among Fig. 1 is a front surface, is the back side with the upper surface among the figure.

[0057] and for example shown in Figure 2, outside cylinder part 42 and inboard cylinder part 43 form thicker and weak point cylindric separately.The outside cylinder part 42 outstanding outer peripheral portions that are arranged on the front surface of runner plate portion 41, its outer circumferential face arrives the outer circumferential face of runner plate portion 41 continuously.The inboard cylinder part 43 outstanding interior circumferential portion that are arranged on the front surface of runner plate portion 41, inner circumferential surface arrives the inner peripheral surface of runner plate portion 41 continuously.The internal diameter of outside cylinder part 42 is formed with cylinder chamber 60,65 greater than the external diameter of inboard cylinder part 43 between outside cylinder part 42 and inboard cylinder part 43.The cross section of this cylinder chamber 60,65 (that is, with the section of the axle direction quadrature of cylinder 40 or the section parallel) with the runner plate portion 41 of cylinder 40 be shaped as ring-type.The front surface of runner plate portion 41 is in the face of this cylinder chamber 60,65.And, the front-end face of outside cylinder part 42 and inboard cylinder part 43 (lower end surface among Fig. 1) all with runner plate portion 51 sliding contacts of second shell 50.

[0058] eccentric part 27 of crankshaft 25 connects cylinder 40.The inner peripheral surface sliding contact of the outer circumferential face of eccentric part 27 and runner plate portion 41 and inboard cylinder part 43.Being entrenched in cylinder 40 in the eccentric part 27 carries out off-centre along with the rotation of crankshaft 25 and rotatablely moves.

[0059] blade 45 forms as one with cylinder 40, is configured to towards the cross-section cylinder chamber 60,65 of the diametric(al) of cylinder chamber 60,65.Specifically, the outer circumferential face of blade 45 from the inner peripheral surface of outside cylinder part 42 to inboard cylinder part 43 forms the planar of extending towards the diametric(al) of cylinder 40, becomes one with outside cylinder part 42 and inboard cylinder part 43.And blade 45 is from the outstanding state of the front surface of runner plate portion 41, also becomes one with runner plate portion 41.

[0060] as mentioned above, piston only 52 is " C " font (with reference to Fig. 2) from the plane.The external diameter of piston only 52 is less than the internal diameter of outside cylinder part 42, and its internal diameter is greater than the external diameter of inboard cylinder part 43.This piston only 52 inserts the state that is formed on the cylinder chamber 60,65 between outside cylinder part 42 and the inboard cylinder part 43 for the below from Fig. 1. Cylinder chamber 60,65 is divided into the outside and the inboard of piston only 52, and the outside of piston only 52 is an outside cylinder chamber 60, and the inboard of piston only 52 is inboard cylinder chamber 65.

[0061] to be configured to its axle center consistent with the axle center of the main shaft part 26 of crankshaft 25 for piston only 52.The inner peripheral surface of the outer circumferential face of this piston only 52 and outside cylinder part 42 is in place sliding contact, and the outer circumferential face of inner circumferential surface and inboard cylinder part 43 is in place sliding contact.Piston only 52 and the position of cylinder part 42 sliding contact parts in the outside with respect to piston only 52 and inboard cylinder part 43 sliding contact parts are the opposition sides that is positioned at the axle center that clips piston only 52, promptly are positioned at the position of 180 ° of phase shiftings.

[0062] and, piston only 52 is configured to the place (with reference to Fig. 2) that blade 45 connects its disconnections.Outside cylinder chamber 60 is divided into hyperbaric chamber 61,66 and low pressure chamber 62,67 by blade 45 respectively with inboard cylinder chamber 65.

[0063] a pair ofly shakes the gap that lining (bush) 56 inserts the side (left and right side among Fig. 2) of the end face of circumferencial direction of piston onlies 52 and blade 45.That is to say, shake the blade 45 of lining 56 in Fig. 2 about respectively dispose one.Respectively shake lining 56 for outer side surface forms arc surface, inner side surface forms the widget on plane.The end face of the circumferencial direction of piston only 52 is an arc surface, slides with the outer side surface that shakes lining 56.And, the side slip of shaking the inner side surface and the blade 45 of lining 56.Shaking lining 56 by this is supported for blade 45 with respect to piston only 52 and rotates freely and free to advance or retreat.

[0064] is formed with through hole 44 in outside cylinder part 42.Through hole 44 is formed near the right side of the blade 45 among Fig. 2, connects outside cylinder part 42 towards diametric(al).This through hole 44 allows the low pressure chamber 62 of outside cylinder chamber 60 be communicated with suction space 57.And, be formed with through hole 53 at piston only 52.Through hole 53 is formed near the right side of the blade 45 among Fig. 2, connects piston only 52 towards diametric(al).This through hole 53 allows the low pressure chamber 67 of inboard cylinder chamber 65 be communicated with the low pressure chamber 62 of outside cylinder chamber 60.

[0065] the runner plate portion 51 at second shell 50 is formed with outside ejection passage 54 and inboard ejection passage 55.Outside ejection passage 54 and inboard ejection passage 55 connect runner plate portion 51 towards thickness direction separately.Front surface in runner plate portion 51, outside ejection passage 54 the position of the close periphery of piston only 52 and with Fig. 2 in blade 45 left side adjoining position upper sheds.And, inboard ejection passage 55 the position in the close interior week of piston only 52 and with Fig. 2 in blade 45 left side adjoining position upper sheds.And outside ejection passage 54 is communicated to the hyperbaric chamber 61 of outside cylinder chamber 60, and inboard ejection passage 55 is communicated to the hyperbaric chamber 66 of inboard cylinder chamber 65.And the outer ejection valve of utilization figure opens, cuts out outside ejection passage 54 and inboard ejection passage 55.

[0066] downside at second shell 50 is equipped with baffler (muffler) 31.This baffler 31 is set to cover second shell 50 from downside, and second shell 50 between be formed with the ejection space 32.And, be formed with in the outer edge of first shell 35 and second shell 50 and allow ejection space 32 be connected to than the connecting path 33 of first shell 35 by the space of upside.

[0067] and for example shown in Figure 3, in compressing mechanism 30, major diameter seal ring 71 and minor diameter seal ring 72 are installed at the plat part 36 of first shell 35.Major diameter seal ring 71 and minor diameter seal ring 72 are embedded in respectively in the groove of front surface (lower surface among Fig. 3) opening of plat part 36.Major diameter seal ring 71 is set to the outside around minor diameter seal ring 72.And major diameter seal ring 71 and minor diameter seal ring 72 push up the back side of the runner plate portion 41 of cylinder 40 respectively.

[0068] and, as shown in Figure 4, the axle center of major diameter seal ring 71 and minor diameter seal ring 72 misalignment piston only 52 separately (that is the axle center of main shaft part 26).The center O of major diameter seal ring 71 ₁Center O with minor diameter seal ring 72 ₂All be partial to hyperbaric chamber 61,66 than the axle center of piston only 52.And major diameter seal ring 71 and minor diameter seal ring 72 central position separately differ from one another.The center O of minor diameter seal ring 72 ₂Center O than major diameter seal ring 71 ₁Near blade 45.

[0069] be formed with very narrow gap between the back side of the runner plate portion 41 of the front surface of the plat part 36 of first shell 35 and cylinder 40, this gap becomes back side gap 75 (with reference to Fig. 3).This back side gap 75 is divided into than the intermediate space 77 between minor diameter seal ring 72 interior side clearance 76, minor diameter seal ring 72 and the major diameter seal ring 71 in the inner part with than major diameter seal ring 71 outer side clearance 78 in the outer part.

[0070] because outer side clearance 78 is communicated with suction space 57, therefore almost the pressure (suction pressure) with the refrigeration agent that is inhaled into compressing mechanism 30 is identical for the interior pressure of outer side clearance 78.And, owing in interior side clearance 76, be full of the lubricant oil that the fuel feeding path via crankshaft 25 provides, therefore in the interior pressure of side clearance 76 almost identical with pressure (ejection pressure) from the refrigeration agent of compressing mechanism 30 ejections.The influence of the interior pressure of side clearance 76 in cylinder 40 is subjected to and be pushed to the below of Fig. 3.Major diameter seal ring 71 and minor diameter seal ring 72 constitutes allows pushing force act on pushing and pressing mechanism 70 on the cylinder 40.And in the present embodiment, cylinder 40 becomes and pushes away side component, becomes as second shell 50 of piston and accepts side component.

[0071] as shown in Figure 3, be provided with controlling mechanism 80 at compressing mechanism 30.Controlling mechanism 80 constitutes by access 81 with for the defferential valve 82 of open and close valve.Access 81 and defferential valve 82 all are set at first shell 35.

[0072] access 81 is for being formed on the thin path of first shell 35.One end of this access 81 is intermediate space 77 openings of side clearance 75 overleaf, and the other end is at the back side of the plat part 36 of first shell 35 (upper surface of Fig. 3) opening.

[0073] defferential valve 82 comprises valve body 83, spring 85 and cover 86.At the plat part 36 of first shell 35, hole 87 is buried at the end that has that is formed with cross-section access 81 underground, and this has the end to bury hole 87 underground to extend towards the below from its back side, bury underground at this and taken in valve body 83, spring 85 and cover 86 in hole 87.Valve body 83 roughly forms cylindric, and is free to advance or retreat towards the axle direction of burying hole 87 underground.And, in the circumferential groove 84 that is formed with near the lower end of valve body 83 at its outer circumferential face opening.Spring 85 is configured between the bottom and valve body 83 of burying hole 87 underground, applies the power of valve body 83 towards the top that makes.Bury underground in the hole 87 than valve body 83 by under the space be communicated with suction passage 39.Cover 86 is set to block the upper end of burying hole 87 underground.And, be formed with the hole of minor diameter at cover 86.Bury underground in the hole 87 and lean on the hole of last space, be communicated with the inner space of the housing 11 that has been full of ejection gas by cover 86 than valve body 83.

[0074] at the valve body 83 of defferential valve 82, ejection pressure acts on its upper surface, and suction pressure and spring 85 applied forces act on its lower surface.Valve body 83 moves up and down according to ejection pressure and differing from of suction pressure.And shown in Fig. 3 (A), when the height of the circumferential groove 84 of valve body 83 arrived the position of access 81, access 81 became open mode.And shown in Fig. 3 (B), when the position of the highly deviated access 81 of the circumferential groove 84 of valve body 83, access 81 becomes closed condition.

[0075]-the running action-

As mentioned above, above-mentioned rotary compressor 10 is set in the refrigerant circuit of refrigerating machine.And this rotary compressor 10 sucks, is compressed in the refrigeration agent that evaporates in the vaporizer, and the gas refrigerant that will become high pressure after will being compressed sprays to condensed device.

[0076] here, with reference to Fig. 5 the action of rotary compressor 10 compressed refrigerants is illustrated.After motor 20 energisings, cylinder 40 is driven by crankshaft 25.Cylinder 40 revolves round the sun towards the clockwise direction among Fig. 5.

[0077] at first, be illustrated refrigeration agent being sucked the process that inboard cylinder chamber 65 compresses.

[0078] when cylinder 40 was only mobile some from the state of Fig. 5 (A), refrigeration agent began to be inhaled into the low pressure chamber 67 of inboard cylinder chamber 65.The refrigeration agent that flows into suction passage 39 passes through the through hole 53 of the through hole 44 of suction space 57, outside cylinder part 42, outside cylinder chamber 60, piston only 52 successively and flows into low pressure chamber 67.And along with cylinder 40 revolution, the volume of low pressure chamber 67 enlarges ((B) with reference to FIG. be (D) (C)), and when returning to the state of scheming (A) together, the suction process that refrigeration agent is inhaled into inboard cylinder chamber 65 finishes.

[0079] further revolve round the sun when cylinder 40, when the sliding contact part of inboard cylinder part 43 and piston only 52 surpassed the through hole 53 of piston only 52, refrigeration agent began to be compressed in the hyperbaric chamber 66 of inboard cylinder chamber 65.And along with cylinder 40 revolution, the volume in hyperbaric chamber 66 dwindles ((B) with reference to FIG. be (D) (C)), and the refrigeration agent in the hyperbaric chamber 66 is compressed.When in this process, the interior pressure in hyperbaric chamber 66 is high to a certain degree the time, and the ejection valve is opened, and inboard ejection passage 55 becomes open state, and the refrigeration agent in hyperbaric chamber 66 sprays to ejection space 32 via inboard ejection passage 55.When returning to the state of scheming (A) together, the ejection processes of 66 ejection refrigeration agents finish from the hyperbaric chamber.

[0080] secondly, the process that cylinder chamber 60 outside refrigeration agent is sucked is compressed is illustrated.

[0081] when cylinder 40 was only mobile some from the state of Fig. 5 (C), refrigeration agent began to be inhaled into the low pressure chamber 62 of outside cylinder chamber 60.The refrigeration agent of inflow suction passage 39 is through hole 44 and the inflow low pressure chamber 62 through sucking space 57, outside cylinder part 42 successively.And along with cylinder 40 revolution, the volume of low pressure chamber 62 enlarges ((D) with reference to FIG. be (B) (A)), and when returning to the state of scheming (C) together, the suction process that refrigeration agent is inhaled into outside cylinder chamber 60 finishes.

[0082] further revolve round the sun when cylinder 40, when the sliding contact part of outside cylinder part 42 and piston only 52 surpassed the through hole 53 of piston only 52, refrigeration agent began to be compressed in the hyperbaric chamber 61 of outside cylinder chamber 60.And along with cylinder 40 revolution, the volume in hyperbaric chamber 61 dwindles ((D) with reference to FIG. be (B) (A)), and the refrigeration agent in the hyperbaric chamber 61 is compressed.When in this process, when the interior pressure height in hyperbaric chamber 61 arrived to a certain degree, the ejection valve was opened, and outside ejection passage 54 becomes open state, and the refrigeration agent in hyperbaric chamber 61 sprays to through outside ejection passage 54 and sprays space 32.When returning to the state of scheming (C) together, the ejection processes of 61 ejection refrigeration agents finish from the hyperbaric chamber.

[0083] sprays to the space of the refrigeration agent in ejection space 32 from inboard cylinder chamber 65 and outside cylinder chamber 60, then, spray to the outside of housing 11 through spraying pipe 14 through connecting path 33 inflows first shell 35 upsides.

[0084] as shown in Figure 3, more total than minor diameter seal ring 72 interior side clearance 76 in the inner part in the running of rotary compressor 10 for spraying pressure, be suction pressure always than major diameter seal ring 71 outer side clearance 78 in the outer part.And the pressure of intermediate space 77 is different because of the state of defferential valve 82.The interior pressure in these back side gaps 75 acts on the back side of the runner plate portion 41 of cylinder 40, with runner plate portion 51 sides (that is, the below of Fig. 3) pushing of cylinder 40 towards second shell 50.Therefore, though hyperbaric chamber 61,66 in press liter, cylinder 40 can not move towards the top yet, and the axial gap of the cylinder 40 and second shell 50 is remained unchanged.

[0085] and, in this rotary compressor 10, the size that controlling mechanism 80 comes down the load of regulating action on cylinder 40 according to the difference of ejection pressure and suction pressure.With reference to Fig. 3 this action is illustrated.

[0086] shown in Fig. 3 (A), under the less operating condition of the difference of ejection pressure and suction pressure, the valve body 83 of defferential valve 82 is pushed to the top by spring 85 applied forces, and access 81 becomes the state of opening.Under this state, be full of from the inner space of the housing 11 of the gas refrigerant of compressing mechanism 30 ejection and be communicated to intermediate space 77 by access 81, the pressure of intermediate space 77 becomes ejection pressure.That is to say that under this state, interior side clearance 76 and intermediate space 77 all become ejection pressure, only have remaining outer side clearance 78 to become suction pressure.Therefore, the area of the part of ejection pressure effect becomes big in the back side of cylinder 40, and the pushing force down that acts on the cylinder 40 is compared with only having interior side clearance 76 to become to spray pressure status, and is bigger.

[0087] like this, less in the difference of ejection pressure and suction pressure, act under the operating condition of pushing force on the cylinder 40 for not enough tendency, will spray pressure and import intermediate space 77, guarantee the load down of countercylinder 40 effects.

[0088] on the other hand, shown in Fig. 3 (B), under the bigger operating condition of the difference of ejection pressure and suction pressure, the valve body 83 of defferential valve 82 overcomes spring 85 applied forces and is given as security downwards, and access 81 becomes closing state.And intermediate space 77 is cut off from the inner space of housing 11, and the pressure of intermediate space 77 becomes the intermediate value of ejection pressure and suction pressure.That is to say owing to be not that major diameter seal ring 71 and minor diameter seal ring 72 stop spilling of fluid fully, so the pressure of intermediate space 77 become in the intermediate value of pressure of the pressure of side clearance 76 and outer side clearance 78.So the area of the part of ejection pressure effect diminishes in the back side of cylinder 40, act on pushing force down on the cylinder 40, all become the ejection pressure status with interior side clearance 76 and intermediate space 77 and compare, diminish.

[0089] by like this, difference in ejection pressure and suction pressure is bigger, act under the operating condition of pushing force for superfluous tendency on the cylinder 40, the pressure that makes intermediate space 77 is cut down the load down of countercylinder 40 effects for pressing in the middle of ejection pressure and the suction pressure.

[0090] here, in above-mentioned rotary compressor 10, the gas pressure that acts in the runner plate portion 41 of cylinder 40 is that hyperbaric chamber 61,66 sides are greater than low pressure chamber 62,67 sides.Therefore, only allow the pushing force mean effort, the moment that allows cylinder 40 tilt is stayed at the back side of the runner plate portion 41 of cylinder 40.

[0091] in the rotary compressor 10 of present embodiment, expected in order to reduce the countermeasure of this moment.That is to say, as mentioned above, in this rotary compressor 10, make major diameter seal ring 71 and minor diameter seal ring 72 deflection hyperbaric chamber 61,66, central position separately.When major diameter seal ring 71 and minor diameter seal ring 72 being configured near hyperbaric chamber 61,66, in the runner plate portion 41 of cylinder 40, act near the pushing force on the part in hyperbaric chamber 61,66 and compare with part near low pressure chamber 62,67, become big.So, reduced the moment that allows cylinder 40 tilt.

[0092] and, in above-mentioned rotary compressor 10, the center that major diameter seal ring 71 and minor diameter seal ring 72 are configured to separately is in different positions.Therefore, in the inboard that minor diameter seal ring 72 is only arranged (promptly, interior side clearance 76 is only arranged) become that ejection pressure status following time acts on the action center of the pushing force on the cylinder 40 and become the position that ejection pressure status following time acts on the action center of the pushing force on the cylinder 40 in the whole inboard of major diameter seal ring 71 (that is, interior side clearance 76 and intermediate space 77) and differ from one another.That is to say that the position that the official post of ejection pressure and suction pressure acts on the action center of the pushing force in the runner plate portion 41 of cylinder 40 changes.

[0093]-first embodiment's effect-

In the present embodiment, allow down pushing force countercylinder 40 effect, will be subjected to the influence of the air pressure in the cylinder chamber 60,65 and the cylinder 40 that will float is up given as security by pushing force.So, in the running of rotary compressor 10, there is not the phenomenon of the axial gap enlargement of the cylinder 40 and second shell 50 yet, can suppression fluid 61,66 spill from the hyperbaric chamber, improve compression efficiency.

[0094] and, in the present embodiment, controlling mechanism 80 comes regulating action in the size as the load of the axle direction (above-below direction) on the cylinder 40 that pushes away side component according to the difference of ejection pressure and suction pressure.Therefore,, also can suitably set the size that acts on the axial load on the cylinder 40, can reduce by the power loss that friction produced between the cylinder 40 and second shell 50 even when the operating condition of rotary compressor 10 changes.

[0095] therefore,, can improve the compression efficiency of rotary compressor 10, simultaneously, reduce the mechanical loss in this running, can seek to improve the performance of rotary compressor 10 according to present embodiment.

[0096] and, according to present embodiment, even the operating condition of rotary compressor 10 changes, the pressure difference of ejecting fluid and suction fluid changes, also can positively cut down the size of the moment that allows tilt as the cylinder 40 that pushes away side component, can avoid problems such as the reduction of the compression efficiency that tilts to cause because of cylinder 40 and eccentric wear damage.

[0097] (second embodiment)

The second embodiment of the present invention is illustrated.The rotary compressor 10 of present embodiment is for having changed the compressor of the structure of controlling mechanism 80 and pushing and pressing mechanism 70 in above-mentioned first embodiment.Here, the rotary compressor 10 of present embodiment and above-mentioned first embodiment's difference are illustrated.

[0098] as shown in Figure 6, the controlling mechanism 80 of present embodiment comprises access 81 and defferential valve 82.And the defferential valve 82 of present embodiment comprises valve body 83, spring 85 and cover 86.About these aspects, the controlling mechanism 80 of present embodiment is the same with above-mentioned first embodiment.But, the access 81 of the controlling mechanism 80 of present embodiment is different with above-mentioned first embodiment with the configuration of defferential valve 82, and, outside access 81 and defferential valve 82, also comprise groove 88.

[0099] groove 88 of above-mentioned controlling mechanism 80 is formed on the piston only 52 in second shell 50.Specifically, groove 88 is formed on the part (being roughly the left-half of Fig. 7) in the close hyperbaric chamber 61,66 in the piston only 52.This groove 88 is the elongated slot of front-end face (upper-end surface of Fig. 7) opening at piston only 52, extends to circular-arc along the prolonging direction of piston only 52.Like this, the face opening that groove 88 runner plate portion 41 in piston only 52 and cylinder 40 is slided.

[0100] access 81 of above-mentioned controlling mechanism 80 is formed into the peripheral portion 38 and second shell 50 of first shell 35.One end of this access 81 is at the inner peripheral surface opening of peripheral portion 38, one distolateral with suck space 57 and be communicated with.And the other end of access 81 is at the bottom surface opening of the groove 88 that is formed on piston only 52.That is to say that this access 81 is connected to groove 88 and sucks space 57.

[0101] valve body 83 of the defferential valve 82 of above-mentioned controlling mechanism 80, spring 85 and cover 86 are embedded in second shell 50.Specifically, in the runner plate portion 51 of second shell 50, hole 87 is buried at the end that has that is formed with cross-section access 81 underground, and this has the end to bury hole 87 underground to extend towards the top from its back side, bury hole 87 underground at this and taken in valve body 83, spring 85 and cover 86.Valve body 83 roughly forms cylindric, and is free to advance or retreat towards the axle direction of burying hole 87 underground.And, be formed with circumferential groove 84 at its outer circumferential face opening in the close upper end of valve body 83 part.Spring 85 is configured between the bottom and valve body 83 of burying hole 87 underground, and valve body 83 is applied power towards the below.The ratio valve body of burying underground in the hole 87 83 is communicated with suction space 57 by last space.Cover 86 is set to block the lower end of burying hole 87 underground.And, be formed with the hole of minor diameter at cover 86.Bury underground in the hole 87 ratio valve body 83 by under the hole of space by cover 86 be communicated with the ejection space 32 that has been full of ejection gas.

[0102] at the valve body 83 of defferential valve 82, ejection pressure acts on its lower surface, and suction pressure and spring 85 applied forces act on its upper surface.Valve body 83 moves up and down according to the difference of ejection pressure and suction pressure.And when the height of the circumferential groove 84 of valve body 83 dropped to the position of access 81, access 81 became open mode.And when the position of the highly deviated access 81 of the circumferential groove 84 of valve body 83, access 81 becomes closed condition.In addition, in Fig. 6, valve body 83 is for having opened the state of access 81.

[0103] in the rotary compressor 10 of present embodiment, only be provided with a seal ring 73 at compressing mechanism 30, this seal ring 73 constitutes pushing and pressing mechanism 70.Sealing ring 73 is the same with minor diameter seal ring 72 with above-mentioned first embodiment's major diameter seal ring 71, is embedded in the groove of lower surface opening of the plat part 36 of first shell 35, withstands on the back side of the runner plate portion 41 of cylinder 40.And the back side gap 75 that sealing ring 73 will be formed between the runner plate portion 41 of the plat part 36 of first shell 35 and cylinder 40 is isolated into the interior side clearance 76 of seal ring 73 inboards and the outer side clearance 78 in its outside.In the running of rotary compressor 10, the interior pressure of interior side clearance 76 remains on ejection pressure, and the interior pressure of outer side clearance 78 remains on suction pressure.

[0104]-the running action-

The size that the controlling mechanism 80 of present embodiment comes down the load of regulating action on cylinder 40 according to the difference of ejection pressure and suction pressure.At that time, this controlling mechanism 80 changes the size that acts on the load down on the cylinder 40 by changing the size for the power that pushes back up of cylinder 40 effects.

[0105] at first, under the less operating condition of the difference of ejection pressure and suction pressure, the valve body 83 of defferential valve 82 is given as security downwards by spring 85 applied forces, and access 81 becomes open mode.Under this state, groove 88 and suction space 57 are connected together by access 81, and the pressure of groove 88 becomes suction pressure.That is to say, under this state, be not fluid pressure action in the hyperbaric chamber 61,66 in runner plate portion 41 front surfaces of cylinder 40, in the face of on the part of groove 88, but suction pressure act in runner plate portion 41 front surfaces of cylinder 40, in the face of on the part of groove 88.Therefore, the size that cylinder 40 be pushed to the power that pushes back of top diminishes, and the load down that acts on the cylinder 40 becomes big.

[0106] like this, difference in ejection pressure and suction pressure is less, acts under the operating condition of pushing force for not enough tendency on the cylinder 40, and suction pressure is imported groove 88, cut down the power that pushes back up that acts on the cylinder 40, guarantee to act on the load down on the cylinder 40.

[0107] on the other hand, under the bigger operating condition of the difference of ejection pressure and suction pressure, the valve body 83 of defferential valve 82 overcomes spring 85 applied forces and is given as security upward, and access 81 becomes closed condition.Under this state, groove cuts off from sucking space 57, the groove 88 that bleeds at leisure of the fluids in the hyperbaric chamber 61,66.And the pressure of groove 88 is compared during for open mode with access 81, uprises.Therefore, the size that cylinder 40 be pushed to the power that pushes back of top becomes big, and the load down that acts on the cylinder 40 diminishes.

[0108] like this, difference in ejection pressure and suction pressure is bigger, act under the operating condition of pushing force on the cylinder 40 for superfluous tendency, make the pressure of groove 88 be higher than suction pressure, increase the power that pushes back up that acts on the cylinder 40, cut down the load down that acts on the cylinder 40.

[0109] in the compressing mechanism 30 of present embodiment, the hydrodynamic pressure that acts on the front surface of runner plate portion 41 of cylinder 40 is that hyperbaric chamber 61,66 sides are greater than low pressure chamber 62,67 sides.And in the present embodiment, allow the part opening in the close hyperbaric chamber 61,66 of groove 88 in the front-end face of piston only 52.And, when suction pressure being imported this groove 88 by access 81, act on the part of hyperbaric chamber 61,66 sides in the runner plate portion 41 of cylinder 40 to push back power less, the moment that allows cylinder 40 tilt diminishes.

[0110]-second embodiment's effect-

In the present embodiment, controlling mechanism 80 is regulated the size for the power that pushes back up of cylinder 40 effects.Therefore, the same during with above-mentioned first embodiment, the size of down the load of regulating action on cylinder 40 exactly.

[0111] and, in the present embodiment, allow groove 88 in the front-end face of piston only 52 near the part opening in hyperbaric chamber 61,66.Therefore, the moment that allows cylinder 40 tilt can be reduced, problems such as the reduction of the compression efficiency that tilts to cause because of cylinder 40 and eccentric wear damage can be avoided.

[0112] (the 3rd embodiment)

The third embodiment of the present invention is illustrated.The rotary compressor 10 of present embodiment is for having changed the compressor of the structure of controlling mechanism 80 in above-mentioned second embodiment.Here, with reference to Fig. 8 and Fig. 9 the controlling mechanism 80 of present embodiment is illustrated.

[0113] in the controlling mechanism 80 of present embodiment, groove 88 is formed on the piston only 52 in second shell 50.This groove 88 is formed on the part (being roughly the right half part of Fig. 9) of the close low pressure chamber 62,67 in the piston only 52.This groove 88 is the elongated slot of front-end face (upper-end surface of Fig. 8) opening at piston only 52, extends to circular-arc along the prolonging direction of piston only 52.Like this, the face opening that groove 88 runner plate portion 41 in piston only 52 and cylinder 40 is slided.

[0114] access 81 of above-mentioned controlling mechanism 80 is formed on second shell 50.One end of this access 81 is at the back side of the runner plate portion 51 of second shell 50 (lower surface of Fig. 8) opening, and one distolaterally is communicated with ejection space 32.And the other end of access 81 is at the bottom surface opening of the groove 88 that is formed on piston only 52.That is to say that this access 81 is connected to ejection space 32 with groove 88.

[0115] valve body 83 of the defferential valve 82 of above-mentioned controlling mechanism 80, spring 85 and cover 86 are embedded in second shell 50.Specifically, in the runner plate portion 51 of second shell 50, hole 87 is buried at the end that has that is formed with cross-section access 81 underground, and this has the end to bury hole 87 underground to extend towards the top from its back side, bury hole 87 underground at this and taken in valve body 83, spring 85 and cover 86.Valve body 83 roughly forms cylindric, and is free to advance or retreat towards the axle direction of burying hole 87 underground.And, be formed with circumferential groove 84 at its outer circumferential face opening in the close upper end of valve body 83 part.Spring 85 is configured between the bottom and valve body 83 of burying hole 87 underground, and valve body 83 is applied power towards the below.The ratio valve body of burying underground in the hole 87 83 is communicated with suction passage 39 by last space.Cover 86 is set to block the lower end of burying hole 87 underground.And, be formed with the hole of minor diameter at cover 86.Bury underground in the hole 87 ratio valve body 83 by under the space, the hole by cover 86 is communicated with the ejection space 32 that has been full of ejection gas.

[0116] at the valve body 83 of defferential valve 82, ejection pressure acts on its lower surface, and suction pressure and spring 85 applied forces act on its upper surface.Valve body 83 moves up and down according to the difference of ejection pressure and suction pressure.And when the height of the circumferential groove 84 of valve body 83 dropped to the position of access 81, access 81 became open mode.And when the position of the highly deviated access 81 of the circumferential groove 84 of valve body 83, access 81 becomes closed condition.In addition, in Fig. 8, valve body 83 is for opening the state of access 81.

[0117]-the running action-

The same with above-mentioned second embodiment, the controlling mechanism 80 of present embodiment changes the size that acts on the load down on the cylinder 40 by changing the size for the power that pushes back up of cylinder 40 effects.

[0118] at first, under the bigger operating condition of the difference of ejection pressure and suction pressure, the valve body 83 of defferential valve 82 overcomes spring 85 applied forces and is pushed to the top, and access 81 becomes open mode.Under this state, groove 88 and ejection space 32 are communicated with, and the pressure of groove 88 becomes ejection pressure.That is to say, under this state, be not fluid pressure action in the low pressure chamber 62,67 in runner plate portion 41 front surfaces of cylinder 40 in the face of on the part of groove 88, but ejection pressure act in runner plate portion 41 front surfaces of cylinder 40 in the face of on the part of groove 88.Therefore, the size that cylinder 40 be pushed to the power that pushes back of top becomes big, and the load down that acts on the cylinder 40 diminishes.

[0119] like this, difference in ejection pressure and suction pressure is bigger, acts under the operating condition of pushing force for superfluous tendency on the cylinder 40, makes the pressure of groove 88 be ejection pressure, increase the power that pushes back up that acts on the cylinder 40, cut down the load down that acts on the cylinder 40.

[0120] on the other hand, under the less operating condition of the difference of ejection pressure and suction pressure, the valve body 83 of defferential valve 82 is given as security downwards by spring 85 applied forces, and access 81 becomes closed condition.Under this state, groove cuts off from ejection space 32, and the gas refrigerant in the groove 88 escapes to low pressure chamber 62,67 at leisure.And the pressure of groove 88 is compared step-down with access 81 during for open mode.Therefore, the size that cylinder 40 be pushed to the power that pushes back of top diminishes, and the load down that acts on the cylinder 40 becomes big.

[0121] like this, difference in ejection pressure and suction pressure is less, act under the operating condition of pushing force on the cylinder 40 for not enough tendency, make groove 88 in force down in the ejection pressure, cut down the power that pushes back up that acts on the cylinder 40, guarantee to act on the load down on the cylinder 40.

[0122] in the compressing mechanism 30 of present embodiment, the hydrodynamic pressure that acts on the front surface of runner plate portion 41 of cylinder 40 is that low pressure chamber 62,67 sides are less than hyperbaric chamber 61,66 sides.And in the present embodiment, allow the part opening of the close low pressure chamber 62,67 of groove 88 in the front-end face of piston only 52.And in the time will spraying pressure by access 81 and import this groove 88, the power that pushes back that acts on the part of low pressure chamber 62,67 sides in the runner plate portion 41 of cylinder 40 becomes big, and the moment that allows cylinder 40 tilt diminishes.

[0123] (other embodiment)

-the first variation-

In above-mentioned first embodiment's compressing mechanism 30, the axle center that allows the center of the center of major diameter seal ring 71 and minor diameter seal ring 72 all depart from main shaft part 26, but also can replace it as shown in figure 10, only allows the center O of major diameter seal ring 71 ₁The axle center of departing from main shaft part 26 is with the center O of minor diameter seal ring 72 ₂Be configured on the axle center of main shaft part 26.

[0124] when such configuration major diameter seal ring 71 and minor diameter seal ring 72, the area that is formed on part intermediate space 77, that be positioned at close hyperbaric chamber 61,66 between major diameter seal ring 71 and the minor diameter seal ring 72 becomes big.And in the runner plate portion 41 of cylinder 40, (that is, pushing force) point of action is near hyperbaric chamber 61,66, and the result can positively cut down the moment that allows cylinder 40 tilt by littler pushing force for the power of accepting because of the interior pressure of intermediate space 77.So, according to this variation, can the slippage loss that will cause because of the pushing force that acts on the cylinder 40 suppress lower in, suppress the inclination of cylinder 40.

[0125]-second variation-

The pressure than major diameter seal ring 71 part (that is outer side clearance 78) in the outer part that above-mentioned first embodiment's compressing mechanism 30 also can constitute in the back side gap 75 becomes ejection pressure.Here, the difference of this variation with above-mentioned first embodiment is illustrated.

[0126] as shown in figure 11, in the compressing mechanism 30 of this variation, suction passage 39 is formed on second shell 50.Interior all sides of the piston only 52 of the terminal of suction passage 39 in the upper surface of second shell 50 and outer circumferential side be opening respectively.

[0127] in above-mentioned compressor structure 30, is formed with ejection at second shell 50 and presses importing road 59.This ejection press import road 59 allow between the outer circumferential face of inner peripheral surface and cylinder 40 of the peripheral portion 38 that is formed on first shell 35 the space and spray space 32 and be communicated with.And, press to ejection pressure in the peripheral portion 38 of first shell 35 and the space between the cylinder 40, constitute ejection and press space 58.

[0128] in above-mentioned compressor structure 30, access 81 is formed into first shell 35 from second shell 50.One end of this access 81 is connected to major diameter seal ring 71 and the part between the minor diameter seal ring 72 (that is, intermediate space 77) in the back side gap 75, and the other end is connected to suction passage 39.And in the defferential valve 82 of this variation, the space of burying valve body 83 downsides in the hole 87 underground is connected to suction passage 39 by access 81.

[0129] under the bigger operating condition of the difference of ejection pressure and suction pressure, the valve body 83 of defferential valve 82 overcomes spring 85 applied forces and is given as security downwards, and access 81 becomes open mode (with reference to Figure 11).Under this state, suction passage 39 is communicated to intermediate space 77 by access 81, and the pressure of intermediate space 77 becomes suction pressure.Therefore, the area of the part of the ejection pressure effect in cylinder 40 back sides diminishes, and acts on pushing force down on the cylinder 40, all becomes the ejection pressure status with interior side clearance 76 and intermediate space 77 and compare, and diminishes.

[0130] like this, bigger in the difference of ejection pressure and suction pressure, act under the operating condition of pushing force on the cylinder 40 for superfluous tendency, the pressure that makes intermediate space 77 is suction pressure, cuts down the load down for cylinder 40 effects.

[0131] on the other hand, under the less operating condition of the difference of ejection pressure and suction pressure, the valve body 83 of defferential valve 82 is pushed to the top by spring 85 applied forces, and access 81 becomes closed condition.And intermediate space 77 is cut off from suction passage 39, and the pressure of intermediate space 77 rises gradually, finally becomes ejection pressure.That is to say, owing to be not that major diameter seal ring 71 and minor diameter seal ring 72 stop spilling of fluid fully, so the pressure of intermediate space 77 equates with the pressure of interior side clearance 76 and the pressure of outer side clearance 78.

[0132] like this, less in the difference of ejection pressure and suction pressure, act under the operating condition of pushing force on the cylinder 40 for not enough tendency, the pressure of intermediate space 77 is risen, guarantee load down for cylinder 40 effects.

[0133]-the 3rd variation-

In the rotary compressor 10 of the various embodiments described above, as shown in figure 12, also compressing mechanism 30 can be configured in the top of motor 20.Here, to this variation being applicable to the situation among above-mentioned first embodiment is illustrated.

[0134] in the rotary compressor 10 of this variation, the inner space of housing 11 is compressed mechanism 30 and is isolated into top and the bottom, and the space of compressing mechanism 30 tops constitutes upside space 16, and the space of its below constitutes lower side space 17.Spraying pipe 14 is connected upside space 16, and suction pipe 15 is connected lower side space 17.

[0135] in the compressing mechanism 30 of this variation, first shell 35 is configured in below (that is, near motor 20), second shell 50 is configured in the top.Be formed with suction passage 39 at first shell 35.This suction passage 39 allows suction space 57 be communicated with lower side space 17.Be formed with the outside ejection passage 54 of outside cylinder chamber 60 usefulness and the inboard ejection passage 55 of inboard cylinder chamber 65 usefulness at second shell 50.The ejection valve 34 that utilization is made of leaf valve opens, cuts out these ejection passages 54,55.Refrigerant compressed is sprayed to the ejection space 32 in the baffler 31 by these ejection passages 63,68 in compressing mechanism 30, then, flows into upside space 16.

[0136] in above-mentioned compressor structure 30, access 81 is formed into first shell 35 from second shell 50.One end of this access 81 is connected to part (that is, intermediate space 77) in the back side gap 75, between major diameter seal ring 71 and the minor diameter seal ring 72, and the other end is connected to ejection space 32.And in the defferential valve 82 of this variation, the space of burying valve body 83 upsides in the hole 87 underground is connected to ejection space 32 by access 81.

[0137] in above-mentioned rotary compressor 10, oil feed pump 28 is installed in the lower end of crankshaft 25.This oil feed pump 28 is made of volume type pump, sucks the refrigerator oil that amasss in housing 11 bottoms, and provides it to compressing mechanism 30.

[0138] in above-mentioned compressor structure 30, in the back side gap 75 than the pressure that presses to the refrigerator oil that offers compressing mechanism 30 in minor diameter seal ring 72 part (that is interior side clearance 76) in the inner part.That is to say, the interior pressure of interior side clearance 76 and the interior pressure of lower side space 17 be suction pressure about equally.And the pressure than major diameter seal ring 71 part (that is outer side clearance 78) in the outer part in the back side gap 75 is that suction pressure equates with the interior pressure that sucks space 57.

[0139] under the less operating condition of the difference of ejection pressure and suction pressure, the valve body 83 of defferential valve 82 is pushed to the top by spring 85 applied forces, and access 81 becomes open mode (with reference to Figure 12).Under this state, ejection space 32 is communicated to intermediate space 77 by access 81, and the pressure of intermediate space 77 becomes ejection pressure.Therefore, the area of part in cylinder 40 back sides, the effect of ejection pressure becomes big, and the pushing force down that acts on the cylinder 40 is compared with the state that intermediate space 77 becomes suction pressure, becomes big.

[0140] like this, less in the difference of ejection pressure and suction pressure, act under the operating condition of pushing force on the cylinder 40 for not enough tendency, will spray pressure and import intermediate space 77, guarantee load down for cylinder 40 effects.

[0141] on the other hand, under the bigger operating condition of the difference of ejection pressure and suction pressure, the valve body 83 of defferential valve 82 overcomes spring 85 applied forces and is given as security downwards, and access 81 becomes closed condition.And intermediate space 77 is cut off from ejection space 32, and the pressure of intermediate space 77 descends gradually, finally becomes suction pressure.That is to say, owing to be not that major diameter seal ring 71 and minor diameter seal ring 72 stop spilling of fluid fully, so the pressure of intermediate space 77 equates with the pressure of interior side clearance 76 and the pressure of outer side clearance 78.So suction pressure acts on the whole back side of cylinder 40, acting on pushing force down and intermediate space 77 on the cylinder 40 becomes the ejection pressure status and compares, and diminishes.

[0142] like this, bigger in the difference of ejection pressure and suction pressure, act under the operating condition of pushing force on the cylinder 40 for superfluous tendency, the pressure that makes intermediate space 77 is suction pressure, cuts down the load down for cylinder 40 effects.

[0143]-the 4th variation-

In the compressing mechanism 30 of the various embodiments described above, adopted second shell 50 that will have piston only 52 to be fixed up, allow cylinder 40 carry out the structure of eccentric rotation, also can be opposite with it, employing is fixed up cylinder 40, allows second shell 50 with piston only 52 carry out eccentric structure of rotating.At this moment, pushing and pressing mechanism 70 allows pushing force towards second shell, 50 effects with piston only 52.That is to say that at this moment, second shell 50 becomes and pushes away side component, cylinder 40 becomes accepts side component.

[0144] in addition, the foregoing description is to be suitable for example of the present invention in itself, and the present invention does not painstakingly limit its suitable thing or its purposes scope.

(industrial utilize possibility)

[0145] as mentioned above, the present invention presses for allowing cylinder and piston relatively carry out eccentric rotary The rotary compressor of contracted flow body is useful.

Claims (4)

1, a kind of rotary compressor, comprise the cylinder (40) that forms cylinder chamber (60,65), with the state eccentric with respect to this cylinder (40) be accommodated in the said cylinder chamber (60,65) piston (50) and in order to said cylinder chamber (60,65) are divided into the blade (45) of hyperbaric chamber (61,66) and low pressure chamber (62,67), this rotary compressor relatively carries out the off-centre rotation by said cylinder (40) and above-mentioned piston (50), the volume of above-mentioned hyperbaric chamber (61,66) and low pressure chamber (62,67) is changed, it is characterized in that:

Be respectively arranged with runner plate portion at the terminal side of said cylinder (40) and the terminal side of above-mentioned piston (50), runner plate portion (51) front surface separately of the runner plate portion (41) of said cylinder (40) and above-mentioned piston (50) clips said cylinder chamber (60,65) toward each other;

A formation in said cylinder (40) and the above-mentioned piston (50) pushes away side component, and another formation is accepted side component;

This rotary compressor comprises: pushing and pressing mechanism (70), the above-mentioned side component that pushes away is pushed towards the above-mentioned runner plate portion that accepts side component, and

Controlling mechanism (80), pressure difference according to suction fluid that is inhaled into above-mentioned low pressure chamber (62,67) and the ejecting fluid that (61,66) spray from above-mentioned hyperbaric chamber, change and act on the above-mentioned size that pushes away on the side component towards the load of the above-mentioned runner plate portion direction of accepting side component

Above-mentioned controlling mechanism (80) acts on the above-mentioned size towards the load of the above-mentioned runner plate portion direction of accepting side component that pushes away on the side component and changes by allowing the masterpiece that pushes back of the direction left from the above-mentioned runner plate portion that accepts side component be used in and above-mentionedly push away on the side component and change the size that this pushes back power, allowing.

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

Above-mentioned controlling mechanism (80) comprises groove (88), this groove (88) with the above-mentioned front-end face opening of accepting side component of the front surface sliding contact of the above-mentioned runner plate portion that pushes away side component, and this controlling mechanism (80) changes the size of the above-mentioned power of pushing back by the interior pressure that changes this groove (88).

3, rotary compressor according to claim 2 is characterized in that:

The part opening of the close above-mentioned low pressure chamber (62,67) of the groove (88) of above-mentioned controlling mechanism (80) in the above-mentioned front-end face of accepting side component;

Above-mentioned controlling mechanism (80) comprises access (81) and open and close valve (82), this access (81) is connected to the space that above-mentioned ejecting fluid exists with above-mentioned groove (88), when this open and close valve (82) surpasses specified value in the pressure difference of above-mentioned ejecting fluid and above-mentioned suction fluid, open above-mentioned access (81), become specified value when following in this pressure difference, close above-mentioned access (81).

4, rotary compressor according to claim 2 is characterized in that:

The groove (88) of above-mentioned controlling mechanism (80) in the above-mentioned front-end face of accepting side component, near the part opening in above-mentioned hyperbaric chamber (61,66);

Above-mentioned controlling mechanism (80) comprises access (81) and open and close valve (82), this access (81) is connected to the space that above-mentioned suction fluid exists with above-mentioned groove (88), when this open and close valve (82) is lower than specified value in the pressure difference of above-mentioned ejecting fluid and above-mentioned suction fluid, open above-mentioned access (81), become specified value when above in this pressure difference, close above-mentioned access (81).

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