CN101354037B - Hermetic compressor - Google Patents
Hermetic compressor Download PDFInfo
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- CN101354037B CN101354037B CN2008102118746A CN200810211874A CN101354037B CN 101354037 B CN101354037 B CN 101354037B CN 2008102118746 A CN2008102118746 A CN 2008102118746A CN 200810211874 A CN200810211874 A CN 200810211874A CN 101354037 B CN101354037 B CN 101354037B
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Abstract
The present invention provides a hermetically sealed compressor. A hermetically sealed rotary compressor 100 including an electrically-driven element 2, a rotary compressing element 4 equipped with a cylinder 41 having a compression chamber 43 and a hermetically sealed container 1 in which oil 8 is stocked, is equipped with an oil path 62 for injecting the oil 8 into the compression chamber 43 when refrigerant is sucked into the compression chamber 43, and an opening/closing valve 80 for opening/closing the oil path 62 in accordance with the discharge pressure of the rotary compressing element 4 or the pressure of the compressed refrigerant compressed by the rotary compressing element 4.
Description
The application be that March 17, application number in 2006 are 200610057493.8 the applying date, denomination of invention divides an application for the application of " hermetic type compressor ".
Technical field
The present invention relates to be used to freeze and the hermetic type compressor of air-conditioning, particularly relate to the COP (coefficient of performance: technology refrigerating capacity/input power) that is used to improve hermetic type compressor.
Background technique
In the past, known closed rotary compressor had been accommodated electrical components, had been driven and the rotation compression member of compressed refrigerant by this electrical components in seal container.In this closed rotary compressor, for example, shown in Japanese kokai publication hei 6-323276 communique, carry out cylinder and cylinder that off-centre rotatablely moves is arranged in the cylinder with keeping predetermined gap, in this cylinder, form the space (so-called pressing chamber) of crescent shape, blade with described cylinder sliding contact is set simultaneously, and because of this blade, the space of described crescent shape is divided into the low pressure chamber side that sucks refrigeration agent and the hyperbaric chamber side of compressed refrigerant with pressure.
But, in closed rotary compressor in the past, exist the sealing in described crescent shape space insufficient, cause the problem of the cooling effectiveness decline of closed rotary compressor.
Summary of the invention
The present invention makes in view of above-mentioned situation, and its purpose is, thereby provides the sealing that improves between cylinder and the cylinder can improve the hermetic type compressor of cooling effectiveness.
Hermetic type compressor of the present invention, the rotation compression member of accommodating electrical components and being driven by described electrical components in seal container is characterized in that, comprising:
Fuel supply line, it is used for supplying with oil;
Oil circuit, it is connected with described fuel supply line, when the pressing chamber in the cylinder that constitutes described rotation compression member sucks refrigeration agent, described oil is injected in the described pressing chamber;
Description of drawings
Fig. 1 is the longitudinal section of structure of the closed rotary compressor of expression the present invention the 1st mode of execution.
Fig. 2 is the longitudinal section that amplifies expression rotation compression member.
Fig. 3 is the plan view of cylinder.
Fig. 4 is the longitudinal section that amplifies oily injection portion of expression and switch valve.
Fig. 5 is the longitudinal section of the closed rotary compressor structure of expression the present invention the 2nd mode of execution.
Fig. 6 is the longitudinal section that amplifies expression rotation compression member.
Fig. 7 is the plan view of cylinder.
Fig. 8 is the longitudinal section that amplifies expression oil circuit and switch valve.
Fig. 9 is the figure of the refrigerating circuit of expression the present invention the 3rd mode of execution.
Figure 10 is the longitudinal section of a form of the closed rotary compressor of expression present embodiment.
Figure 11 is the longitudinal section that amplifies expression rotation compression member.
Figure 12 is the plan view of cylinder.
Figure 13 is the longitudinal section that amplifies the expression oil circuit.
Figure 14 is the figure of the refrigerating circuit of expression modified example of the present invention.
Embodiment
Embodiment of the present invention is described with reference to the accompanying drawings.
[the 1st mode of execution]
Fig. 1 is the longitudinal section of a form of the closed rotary compressor 100 of expression present embodiment, and Fig. 2 is the longitudinal section that amplifies expression rotation compression member.This closed rotary compressor 100 is connected with pipe arrangement between the condenser of refrigeration agent and the vaporizer and is constituted the closed rotary compressor of refrigerator unit.As shown in Figure 1, this closed rotary compressor has seal container 1, accommodate electrical components 2 at the upside of this seal container 1, accommodate by bent axle 3 drivings of this electrical components 2 and the rotation compression member 4 that this refrigeration agent is compressed at the downside of seal container 1.
Main bearing 7A is fixed in the inner side surface of seal container 1, supports cylinder 41 by this main bearing 7A in seal container 1.In addition, the last side opening of cylinder 41 is by main bearing 7A obturation, and open lower side thus, forms pressing chamber 43 by supplementary bearing 7B obturation in cylinder 41.
In pressing chamber 43, the cylinder 45 that cooperates and carry out eccentric rotation with eccentric part 44 integrally formed on bent axle 3 is set.In addition, as shown in Figure 3, on cylinder 41, form the suction port 48 and the exhaust port 40 of refrigeration agent.The blade groove 47 that radially extends to cylinder 41 is set between suction port 48 and exhaust port 40, in blade groove 47, blade 46 can be set with being free to slide.This blade 46 is by force application components such as springs and often be pressed against on the cylinder 45, when cylinder 45 eccentric rotations, outer circumferential face sliding contact with cylinder 45, in blade groove 47, come and go simultaneously and move, play the effect that the inside of pressing chamber 43 is divided into low pressure chamber side 43A and hyperbaric chamber side 43B according to pressure.
In more detail, the columned space in the cylinder 41, be that the pressing chamber 43 of refrigeration agent disposes cylinder 45 by eccentric this cylinder 41 in, thereby form crescent shape.And because the side face butt of blade 46 and cylinder 45, the pressing chamber 43 of crescent shape is divided into the hyperbaric chamber side 43B of exhaust port 40 sides of the low pressure chamber side 43A of suction port 48 sides of refrigeration agent and refrigeration agent.
As above-mentioned shown in Figure 1, in the suction port 48 of cylinder 41, insert and cooperate suction pipe 6, this external described exhaust port 40 shown in Figure 3 is provided with expulsion valve, and when the refrigerant pressure of hyperbaric chamber side 43B arrived by the head pressure of expulsion valve regulation, refrigeration agent just was discharged in the seal container 1 from exhaust port 40.
Promptly, in closed rotary compressor 100, drive bent axle 3 rotations by electrical components 2, thereby make cylinder 45 eccentric rotation in pressing chamber 43, thus, be inhaled into the low pressure chamber side 43A of pressing chamber 43 by suction pipe 6 by the outer refrigeration agent of supplying with of liquid-storage container 5 slaves, this refrigeration agent moves to hyperbaric chamber side 43B, be compressed simultaneously, be discharged in the seal container 1 from exhaust port 40 then, be discharged to outside the machine from discharge tube 13.
As above-mentioned illustrated in figures 1 and 2, in the degree of the bottom storage of seal container 1 oil 8 to the lower surface (representing with A-A ' line in by figure) of the liquid level arrival main bearing 7A of this oil 8, be provided as the oil header 50 of oil supplying device at the underpart of bent axle 3 3A, this oil header 50 supplies to main bearing 7A, supplementary bearing 7B and rotation compression member 4 to described oily 8 respectively and the sliding parts of part of the sliding friction between the bent axle 3 and rotation compression member 4.
In detail, bent axle 3 forms cylindric, is pressed into oil header 50 cylindraceous at its underpart 3A.As shown in Figure 2, in the inside of oil header 50, the oar 51 of integrally formed formation spirality oil stream.When bent axle 3 rotations, rotation along with oar 51, pick up the oil 8 that is stored in the seal container 1 by centrifugal force from the lower end 50A of oil header 50, through the oil supply hole 52 that oil header 50 upper end side of associating wear, offer each sliding friction part of main bearing 7A, supplementary bearing 7B and rotation compression member 4 and bent axle 3 as lubricant oil.
But described cylinder 45 is in order to prevent when off-centre is rotated and the wearing and tearing of cylinder 41, with inner side surface 49 position contacting of cylinder 41, and keep predetermined gap between the inner side surface 49 of cylinder 41.But because this gap, the sealing of the pressing chamber 43 particularly sealing between low pressure chamber side 43A and the hyperbaric chamber side 43B becomes insufficient, if do not implement any countermeasure, can cause the decline of cooling effectiveness.
Therefore, the closed rotary compressor 100 of present embodiment is configured tool when oriented pressing chamber 43 sucks refrigeration agents, be injected into the oil injection portion 60 of pressing chamber 43 being stored in oil 8 in the seal container 1.Because oil 8 is injected into pressing chamber 43, thus between cylinder 45 and cylinder 41, form oil film, thus improve sealing.This oil injection portion 60 is described in detail in detail below.
As shown in Figure 2, oily injection portion 60 is constituted as oily reservoir 61 with oil in reserve 8, the oil 8 that is stored in oily reservoir 61 is directed to the structure of oil circuit 62 of the pressing chamber 43 of cylinder 41.
On the sliding friction surface of main bearing 7A and bent axle 3, be provided with along the space of the ring-type of the outer circumferential face of this bent axle 3, form oily reservoir 61.Therefore, each sliding friction between described oil header 50 pairs of rotations compression member 4 and the bent axle 3 has partly supplied with at oily 8 o'clock, and the part of its oil 8 is stored in the oily reservoir 61.
Describe in detail, as shown in Figure 4, oil circuit 62 constitutes by the auxiliary oil circuit 63 that forms in main bearing 7A with at the working connection that is communicated to this auxiliary oil circuit 63 64 that cylinder 41 forms.
And, position welding from the outside of seal container 1, when being fixed on main bearing 7A on the seal container 1, the outside at seal container 1, the position P corresponding with the opening end 65A of the 1st oil circuit 65 of main bearing 7A outer circumferential face side positioned welding, thereby can be when fixed main shaft holds 7A, make opening end 65A be close to seal container 1 inner side surface and with opening end 65A obturation.Thus, the other inaccessible member that is used for need not be used, just opening end 65A can be closed, so can realize the simplification of cost degradation, assembling operation operation.In addition, when not being is fixed on structure on the seal container 1 with main bearing 7A, but when cylinder 41 is fixed on structure on the seal container 1, use the opening end 65A of inaccessible the 1st oil circuit 65 such as stopper.
Described working connection 64 is a stria, and this stria is arranged on the upper surface of cylinder 41, and the one end is communicated with the opening end of described the 2nd oil circuit 66, and the other end is communicated with pressing chamber 43, and the oil 8 that guides from auxiliary oil circuit 63 is directed into pressing chamber 43 through working connections 64.In addition, along with the suction of refrigeration agent to the low pressure chamber side 43A of pressing chamber 43, the oil 8 that is stored in the oily reservoir 61 injects pressing chamber 43, so as shown in Figure 3, an end 64A of working connection 64 is at cylinder inside face 49 openings of low pressure chamber side 43A.
Promptly, the head pressure of refrigeration agent (for example 3MPa) acts on the oil 8 in the seal container 1, so the end 64A by making working connection 64 is at low pressure chamber side 43A opening, in the suction step of refrigeration agent, the oil 8 that is stored in the high pressure in the oily reservoir 61 by with the pressure reduction of the interior pressure (for example 1.1MPa) of the low pressure chamber side 43A of pressing chamber 43, through the oil circuit 62 that constitutes by auxiliary oil circuit 63 and working connection 64, be directed into the low pressure chamber side 43A of the pressing chamber 43 of cylinder 41.
This result, along with the suction of refrigeration agent, oil 8 is injected in the pressing chamber 43, so form sufficient oil film by oil 8 between cylinder inside face 49 and cylinder 45, can improve sealing.Particularly, because in the step in refrigeration agent suction pressing chamber 43, inject oil 8, the low pressure chamber side 43A and the hyperbaric chamber side 43B that separate pressing chamber 43 more reliably, so move and in the compressed process (compression step) to hyperbaric chamber side 43B at refrigeration agent, can prevent the leakage of compressed refrigerant, can improve the compression efficiency of refrigeration agent, and can seek the raising of closed rotary compressor 100 cooling effectivenesss to low pressure chamber side 43A.
And, as shown in Figure 3, reference line L with the central point O that connects suction port 48 and cylinder 41A is a benchmark, at the angle θ 1～θ 2 of regulation (θ 1:0 °, θ 2:170 °, be more preferably θ 1:125 °, θ 2:165 °) scope split shed ground form an end 64A of working connection 64, thereby can further improve the compression efficiency (being about 125 °) of refrigeration agent in example shown in Figure 3.
At this, sectional area (opening area) D of the working connection 64 of inner side surface 49 upper sheds by being adjusted at cylinder can adjust the amount of the oil 8 that injects pressing chamber 43.In the present embodiment, for the amount that makes the oil 8 that injects pressing chamber 43 is only amount, thus decision sectional area D, so that the ratio R of the eliminating volume V of the sectional area D of working connection 64 and pressing chamber 43 (=D/V) locate within the limits prescribed.
Specifically, when described ratio R was too small, working connection 64 became narrow, and oil 8 can not inject in the pressing chamber 43, in contrast, when described ratio R is excessive, to excessively injecting oil 8 in the pressing chamber 43, produced liquid compression.Therefore, in the present embodiment, be in 0.004～0.03 (mm by making described ratio R
2/ cc) scope is determined the sectional area D of working connection 64 according to this ratio R, thereby can prevent the liquid compression that the excessive injection of oil 8 causes, can improve the sealing between cylinder inside face 49 and the cylinder 45 simultaneously.
But, in high-frequency region, be driven, compare during high speed rotating with rotation compression member 4, (for example be driven among the 15Hz～30Hz), discharge and press and suck the pressure reduction of pressing hour, it is bigger to inject the sealing effect that oil obtained to pressing chamber 43 at low frequency region.That is, by the injection oil of pressing chamber 43 being limited to pressure reduction hour, can suppress the consumption of the oil 8 that stores in the seal container 1, and can seek the raising of cooling effectiveness efficiently.Therefore, adopt following structure in the present embodiment: switch valve 80 is set, when only the pressure reduction of pressing with low speed rotation, discharge pressure and suction in rotation compression member 4 diminishes, makes switch valve 80 become connected state, oil 8 is injected into pressing chamber 43 in oil circuit 62.
The structure of switch valve 80 below is described in detail in detail, as shown in Figure 4, in main bearing 7A and cylinder 41, is provided with from the 1st oil circuit 65 and crosses working connection 64 and penetrate into the columned through hole 70 of cylinder 41 lower surfaces, described switch valve 80 is set in this through hole 70.Switch valve 80 has to insert and is engaged in the valve body 81 roughly cylindraceous in the through hole 70 and is arranged in the valve body 81 and applies the spring 82 as force application component of elastic force towards 65 pairs of valve bodies 81 of the 1st oil circuit.The top 81A of valve body 81 enters the 1st oil circuit 65, is head pressure to the pressure in this top 81A effect the 1st oil circuit 65.At this moment, the top 81A of valve body 81 forms the shape than through hole 70 diameter reduction, even top 81A is positioned at the 1st oil circuit 65, still can guarantee the stream of oil 8.
In the periphery of valve body 81, form stria 83 along circumferencial direction, to be pushed to by spring 82 at valve body 81 under the state (connected state) of the 1st oil circuit 65 sides, the working connection 64 that is cut off by through hole 70 is connected by the stria 83 of valve body 81, carries out injecting oil to pressing chamber 43.
In addition, as shown in Figure 3, form the connectivity slot 71 that extends to through hole 70 from suction port 48, the suction pressure of refrigeration agent is directed to the bottom of through hole 70 by this connectivity slot 71 at the lower surface of cylinder 41.That is, the pressure (promptly rotating the head pressure of compression member 4) in the top of valve body 81 81A effect the 1st oil circuit 65, the suction pressure of the inboard effect refrigeration agent of this external valve body 81.
Therefore, the head pressure of rotation compression member 4 is low, with the pressure reduction of suction pressure little during, by the elastic force of spring 82 valve body 81 is pushed to the 1st oil circuit 65 sides, become state that working connection 64 connects by the stria 83 of valve body 81, be connected state.In addition, when the pressure reduction of head pressure raising, head pressure and suction pressure of rotation compression member 4 became big, the elastic force of antagonistic spring 82 pushed valve body 81, become the stria 83 of valve body 81 and working connection 65 the state that is connected disconnection, be off state.Under this off state, oil circuit 62 is disconnected, and stops to inject oil 8 to pressing chamber 43.
Thus, to pressing chamber 43 inject that oil is limited at that rotation compression member 4 is driven at low frequency range, the pressure reduction of head pressure and suction pressure hour, can suppress to be stored in the consumption of the oil 8 in the seal container 1, high efficiency seeks to improve cooling effectiveness simultaneously.
As mentioned above,, adopt,, can improve sealing so between cylinder 41 and cylinder 45, form sufficient oil film by the oil 8 that is injected into pressing chamber 43 when pressing chamber 43 sucks refrigeration agent, the structure of oil 8 injection pressing chambers 43 according to present embodiment.Thus, can prevent that the refrigeration agent in the compression step from leaking to low pressure chamber side 43A, thus compression efficiency can be improved, thus can improve the cooling effectiveness of closed rotary compressor 100.
In addition, according to present embodiment, because the ratio of the sectional area D of the working connection 64 of formation oil circuit 62 and the eliminating volume V of pressing chamber 43 is in the scope of regulation, so can prevent the liquid compression that the excessive injection of oil 8 causes, and can improve the sealing between cylinder inside face 49 and the cylinder 45.
And, according to present embodiment, owing to adopt the structure that switch valve 80 is set in oil circuit 62, this switch valve 80 only when the head pressure of rotation compression member 4 is low, rotate in the little zone of the pressure reduction of the head pressure of compression member 4 and suction pressure and be driven the interval, become connected state, so to pressing chamber 43 inject oil be limited at the pressure reduction of the head pressure of rotation compression member 4 and suction pressure little during carry out, thus, can suppress to be stored in the consumption of the oil 8 of seal container 1, and can high efficiency seek to improve cooling effectiveness.
And, in the present embodiment, exemplified closed rotary compressor 100, but be not limited thereto with 1 cylinder 41, also can in closed rotary compressor, use the present invention certainly with 2 cylinders.
[the 2nd mode of execution]
Fig. 5 is the longitudinal section of a form of the closed rotary compressor 100A of expression present embodiment, and Fig. 6 is the longitudinal section that amplifies expression rotation compression member.Closed rotary compressor 100A is connected the closed rotary compressor that constitutes refrigerator unit between the condenser of refrigeration agent and the vaporizer with pipe arrangement.As shown in Figure 5, identical with the closed rotary compressor 100 of the 1st mode of execution, this closed rotary compressor has seal container 1, accommodate electrical components 2 at the upside of this seal container 1, accommodate by bent axle 3 drivings of electrical components 2 and the rotation compression member 4 that refrigeration agent is compressed at the downside of this seal container 1.
And, as shown in Figure 5 and Figure 6, the closed rotary compressor 100A of present embodiment, its basic structure and the 1st mode of execution are same, thus for the general member of the 1st mode of execution, mark identical reference character, omit its explanation.
The closed rotary compressor 100A of present embodiment is in order to improve the compression efficiency of refrigeration agent, and is identical with the 1st mode of execution, adopts the structure of oil 8 being injected pressing chamber 43 when pressing chamber 43 sucks refrigeration agent.Below, specify this structure.
As shown in Figure 8, the upper and lower surface of cylinder 41 be formed for respectively with the surface of contact of main bearing 7A and supplementary bearing 7B in improve end difference 270A, the 270B of fitting tightly property.
In addition, lower surface at the end difference 270B of downside, the cylinder 41 that promptly contacts with supplementary bearing 7B, form the groove 261 that radially extends by cutting, by groove 261, when end difference 270B and supplementary bearing 7B fit tightly, form oil circuit 260, this oil circuit 260 one end 260A are at inner side surface 49 place's openings of cylinder 41, oil 8 split sheds that its other end 260B stores in seal container 1.And, when oil in reserve 8 in the seal container 1 is immersed in the degree of oil in 8 to main bearing 7A, also can form described groove 261 and formation oil circuit 260 at the upper surface of the end difference 270A of upside, the cylinder 41 that promptly contact with main bearing 7A.
Along with the suction of refrigeration agent to pressing chamber 43, inject pressing chamber 43 in order to make oil 8, an end 260A of this oil circuit 260 is at cylinder inside face 49 openings of low pressure chamber side 43A.Particularly, as shown in Figure 7, one end 260A of oil circuit 260 is a benchmark with the reference line L of the central point O of connection suction port 48 and cylinder 41, at the angle θ 1～θ 2 of regulation (θ 1:0 °, θ 2:170 °, be more preferably θ 1:125 °, θ 2:165 °) scope split shed (being about 125 ° in illustrated embodiment).
Promptly, because the head pressure (for example 3MPa) of refrigeration agent acts on the oil 8 in the seal container 1, so an end 260A of oil circuit 260 is at cylinder inside face 49 place's openings of low pressure chamber side 43A, thereby at refrigeration agent in the suction step of pressing chamber 43, the oil 8 of this high pressure by with the pressure reduction of the interior pressure (for example 1.1MPa) of the low pressure chamber side 43A of pressing chamber 43, through oil circuit 260, be injected into the low pressure chamber side 43A of the pressing chamber 43 of cylinder 41.
Thus,, between cylinder inside face 49 and cylinder 45, form sufficient oil film, improve sealing by this oil film by the oil 8 that pressing chamber 43 is injected.Especially, be inhaled at refrigeration agent and inject oil 8 in the step of pressing chamber 43, the low pressure chamber side 43A and the hyperbaric chamber side 43B that can separate pressing chamber 43 more reliably, so at refrigeration agent in the compressed process of hyperbaric chamber side 43B (compression step), can prevent that compressed refrigerant from leaking to low pressure chamber side 43A, can improve the compression efficiency of refrigeration agent, therefore can seek to improve the cooling effectiveness of closed rotary compressor 100A.
At this, in the present embodiment, the sectional area D (being the sectional area of groove 261) of the oil circuit 260 by being adjusted at cylinder inside face 49 openings, the oil mass that adjustment is injected pressing chamber 43, at this moment, the sectional area D that determines oil circuit 260 make the eliminating volume V of itself and pressing chamber 43 ratio R (=D/V) locate within the limits prescribed.Particularly, when described ratio R was too small, oil circuit 260 became narrow, and oil 8 can not inject in the pressing chamber 43; And in contrast, when described ratio R is excessive,, produce liquid compression to excessively injecting oil 8 in the pressing chamber 43.Therefore, by making described ratio R be in 0.004～0.03 (mm
2In/cc) the scope, thereby the liquid compression that the excessive injection of oil 8 causes can be prevented, the sealing between cylinder inside face 49 and the cylinder 45 can be improved simultaneously.
But, in high-frequency region, be driven, compare during high speed rotating with rotation compression member 4, low frequency region (for example be driven among the 15Hz～30Hz), the pressure reduction of head pressure and suction pressure hour, sealing effect from oil to pressing chamber 43 that inject is bigger.That is,, can suppress to be stored in the consumption of the oil 8 of seal container 1, and can high efficiency seek to improve cooling effectiveness by being limited to pressure reduction hour inject oil to pressing chamber 43.Therefore in the present embodiment, employing has in described oil circuit 260 switch valve 280 is set, only by the pressure of the compressed refrigerant of rotation compression member 4 compression hour, promptly only in the head pressure of rotation compression member 4 hour, switch valve 280 becomes connected state, injects the structure of oil 8 to pressing chamber 43.
If describe the structure of switch valve 280 in detail, then (thickness direction) connects, crosses the columned through hole 271 of oil circuit 260 about being provided with on the cylinder 41, and described switch valve 280 is set in this through hole 271.Switch valve 280 has and is inserted in the valve body 281 roughly cylindraceous in the through hole 271 and is arranged in this valve body 281 and as the spring 282 that valve body 281 is applied the force application component of power towards main bearing.By the elastic force of spring 282, push at valve body 281 under the state (connected state) of main bearing 7A side, between the upper surface of the bottom of valve body 281 281A and supplementary bearing 7B, produce the gap, be communicated with the oil circuit 260 that has cut off by through hole 271, inject oil to pressing chamber 43.
In addition, on main bearing 7A, recess 272 is set accordingly with through hole 271.When valve body 281 has been pushed to by spring 282, become the state of the upper surface butt of the top 281B of valve body 281 and recess 272.The end that the compressed refrigerant that is provided with in main bearing 7A imports road 290 connects this recess 272, and the other end that imports road 290 at compressed refrigerant connects the ingress pipe 291 that connects seal container 1 and be fixed.As above-mentioned shown in Figure 5, the part of the compressed refrigerant of discharging from the discharge tube 13 of seal container 1 is directed to ingress pipe 291 by connecting tube, imports road 290 through overcompression, at the pressure of the top of valve body 281 281B effect compressed refrigerant.In addition, determine the spring constant (elastic force) of described spring 282, make pressure reduction when the pressure of compressed refrigerant and suction pressure become specified value or specified value when above, push valve body 281.
Therefore, the pressure difference of compressed refrigerant little during, by the elastic force of spring 282, valve body 281 is pulled to main bearing 7A side, becoming the state that connects oil circuit 260 is connected state.In addition, when the pressure of compressed refrigerant improves, when increasing with the pressure reduction of suction pressure, the elastic force by the pressure antagonistic spring 282 of compressed refrigerant pushes valve body 281, closes oil circuit 260 by the bottom 281A of valve body 281, stops the injection of the oil 8 of pressing chamber 43.
Thus, to pressing chamber 43 inject that oil is limited at that rotation compression member 4 is driven with low frequency, the pressure of compressed refrigerant hour, promptly rotate the pressure reduction of the head pressure of compression member 4 and suction pressure little during, can suppress the consumption of the oil 8 of storage in the seal container 1, can high efficiency improve cooling effectiveness.
As mentioned above, identical according to present embodiment with the 1st mode of execution, adopt in the structure of in the step of the suction refrigeration agent of pressing chamber 43, injecting oil 8, so the oil 8 that injects by pressing chamber 43 to pressing chamber 43.Between cylinder 41 and cylinder 45, form sufficient oil film, can improve sealing.Thus, can prevent in pressing chamber 43 that the refrigeration agent in the compression step from leaking to low pressure chamber side 43A, thus compression efficiency can be improved, thereby can improve the cooling effectiveness of closed rotary compressor 100A.
In addition, according to present embodiment, because being used in the ratio that injects the eliminating volume V of the sectional area D of oil circuit 260 of oil 8 and pressing chamber 43 to pressing chamber 43 is in the predetermined range, so can prevent the liquid compression that the excessive injection of oil 8 causes, can improve the sealing between cylinder inside face 49 and the cylinder 45 simultaneously.
And, according to present embodiment, owing to adopt the structure that switch valve 280 is set in oil circuit 262, this switch valve 280 only the pressure of compressed refrigerant hour, promptly only in the little zone of the pressure reduction of the head pressure of rotation compression member 4 and suction pressure driven during, become connected state, so inject the pressure reduction hour that oil is limited at the head pressure of rotation compression member 4 and suction pressure to pressing chamber 43, thus, can suppress the consumption of the oil 8 of storage in the seal container 1, can high efficiency improve cooling effectiveness simultaneously.
And, in the present embodiment, exemplified closed rotary compressor 100A, but be not limited thereto with 1 cylinder 41, can certainly in closed rotary compressor, use the present invention with 2 cylinders.
[the 3rd mode of execution]
Fig. 9 is the figure of structure that schematically represents the refrigerating circuit 1200 of present embodiment.As shown in Figure 9, connect closed rotary compressor 100B, condenser 1110, expansion valve 1120 and vaporizer 1130 successively by refrigerant pipe 1140, they constitute refrigerating circuit 1200 (refrigeration cycle).In refrigerating circuit 1200, by the refrigeration agent of the gaseous state of the High Temperature High Pressure of closed rotary compressor 100B compression by condenser 1110 heat radiations behind the condensation liquefaction, by expansion valve 1120 decompressions, absorb outside heat by vaporizer 1130 and evaporate, cooling off around the vaporizer 1130.Keep liquid refrigerant by not shown liquid-storage container then, gas refrigerant is got back to closed rotary compressor 100B.
Figure 10 is the longitudinal section of a form of the closed rotary compressor 100B of expression present embodiment, and Figure 11 is the longitudinal section that amplifies expression rotation compression member.This closed rotary compressor 100B is connected between the condenser and vaporizer of refrigeration agent with pipe arrangement, constitute refrigerator unit, as shown in figure 10, identical with the 1st mode of execution with the 2nd mode of execution, this closed rotary compressor 100B has seal container 1, accommodate electrical components 2 at the upside of seal container 1, accommodate by bent axle 3 drivings of electrical components 2 and the rotation compression member 4 that refrigeration agent is compressed at the downside of seal container 1.And, because the basic structure of the closed rotary compressor 100B of present embodiment is identical with the 1st and the 2nd mode of execution, thus for the general member of the 1st and the 2nd mode of execution, mark identical reference character, omit its explanation.
The closed rotary compressor 100B of present embodiment is provided with when the oil circuit 360 that is used for oil 8 is injected to pressing chamber 43 when pressing chamber 43 sucks refrigeration agent in order to improve the compression efficiency of refrigeration agent.Below specify this structure.
As shown in figure 13, oil circuit 360 has the working connection 362 in the auxiliary oil circuit 361 that forms on the main bearing 7A, formation on cylinder 41.
The recess 364 that auxiliary oil circuit 361 has the cross-drilled hole 363 that forms to bent axle 3 sides from the outer circumferential face of main bearing 7A and the bottom surface that is arranged on main bearing 7A and is connected with the bent axle 3 side end 363A of cross-drilled hole 363.
In addition, connect ingress pipe 371 at the main bearing 7A of cross-drilled hole 363 side end 363B, this ingress pipe 371 is fixed on the seal container 1.As shown in figure 10, an end of fuel supply line 372 is connected in this ingress pipe 371; The other end of this fuel supply line 372 is connected on the delivery line 373, and this delivery line 373 is fixed in the bottom of seal container 1.Thus, the oil 8 that is stored in the seal container 1 is supplied with oil by 372 pairs of auxiliary oil circuits of fuel supply line 361.
In addition, as shown in figure 13, working connection 362 forms stria, and the one end is communicated with the opening end that main bearing 7A goes up the recess 364 that forms; The other end extends to pressing chamber 343 and is communicated with.The oil 8 that has been directed into auxiliary oil circuit 361 is directed into pressing chamber 43 through working connection 362.In addition, in order to make along with refrigeration agent injects suction from pressing chamber 43 to the low pressure chamber side 43A of pressing chamber 43, oil 8, as shown in figure 12, an end 362A of working connection 362 is at cylinder inside face 49 openings of low pressure chamber side 43A.
Promptly, because the head pressure (for example 3MPa) of refrigeration agent acts on the oil 8 in the seal container 1, so that an end 362A of working connection 362 at cylinder inside face 49 openings of low pressure chamber side 43A, in the suction step of refrigeration agent, by with the pressure reduction of the interior pressure (for example 1.1MPa) of the low pressure chamber side 43A of pressing chamber 43, the oil 8 of high pressure offers oil circuit 360 by described fuel supply line 372, is injected into the low pressure chamber side 43A of the pressing chamber 43 of cylinder 41 from this oil circuit 360.
This result, along with sucking refrigeration agent to pressing chamber, oil 8 injects pressing chamber 43, so formed sufficient oil film and improved sealing between cylinder inside face 49 and cylinder 45 by oil 8.
Thus, in the pressing chamber 43 of cylinder 41, can separate low pressure chamber side 43A and hyperbaric chamber side 43B more reliably, so the refrigeration agent in sucking low pressure chamber side 43A moves to hyperbaric chamber side 43B in the compressed process (compression step), can prevent that compressed refrigerant from leaking to low pressure chamber side 43A, can improve the compression efficiency of refrigeration agent, therefore can improve the cooling effectiveness of closed rotary compressor 100B.
And, as shown in figure 12, one end 360A of oil circuit 360 is a benchmark with the reference line L of the central point O of connection suction port 48 and cylinder 41, at the angle θ 1～θ 2 of regulation (θ 1:0 °, θ 2:170 °, be more preferably θ 1:125 °, θ 2:165 °) the scope split shed, thereby can further improve the compression efficiency (being about 125 °) of refrigeration agent in illustrated embodiment.
In addition, identical with the 1st mode of execution in the present embodiment, make the eliminating volume V of sectional area (opening area) D of working connection 362 and pressing chamber 43 ratio R (=D/V) locate within the limits prescribed, for example, be in 0.004～0.03 (mm
2In/cc) the scope, thus, can prevent the liquid compression that the excessive injection of oil 8 causes, and improve the sealing between cylinder inside face 49 and the cylinder 45.
But, in high-frequency region, be driven, compare during high speed rotating with rotation compression member 4, low frequency region (for example be driven among the 15Hz～30Hz), the pressure reduction of head pressure and suction pressure hour, sealing effect from oil to pressing chamber 43 that inject is bigger.That is,, can suppress to be stored in the consumption of the oil 8 in the seal container 1, can high efficiency improve cooling effectiveness simultaneously by being limited to pressure reduction hour inject oil to pressing chamber 43.
Therefore, in the present embodiment, as Fig. 9 and shown in Figure 10, solenoid valve 380 is inserted in the fuel supply line 372.In addition, as shown in Figure 9, the control gear 1150 of drive controlling closed rotary compressor 100B comes the switch of control electromagnetic valve 380 according to the driver frequency of rotation compression member 4.This control gear 1150 only low frequency region (when for example driving electrical components 2 among the 15Hz～30Hz), promptly only the pressure reduction of head pressure and suction pressure little during, make solenoid valve 380 be connected state.
Thus, when pressing chamber 43 injects low frequency that oil is limited at closed rotary compressor 100B and drives, only rotate the pressure reduction of the head pressure of compression member 4B and suction pressure little during, the consumption of the oil 8 in the seal container 1 can be suppressed to be stored in, cooling effectiveness can be efficiently improved simultaneously.
As mentioned above, according to present embodiment, identical with the 1st and the 2nd mode of execution, employing is in the step of pressing chamber 43 suction refrigeration agents, the structure of oil 8 injection pressing chambers 43, so formed sufficient oil film and improved sealing between cylinder 41 and cylinder 45 by the oil 8 that is injected in the pressing chamber 43.Thus, can prevent that in pressing chamber 43 refrigeration agent in the compression step from leaking to low pressure chamber side 43A,, therefore can improve the cooling effectiveness of closed rotary compressor 100B so can improve compression efficiency.
In addition, according to present embodiment, because being used in the ratio that injects the eliminating volume V of the sectional area D of oil circuit 360 of oil 8 and pressing chamber 43 to pressing chamber 43 is in the predetermined range, so can prevent the liquid compression that the excessive injection of oil 8 causes, and can improve the sealing between cylinder inside face 49 and the cylinder 45.
And, according to present embodiment, employing is provided with the structure of solenoid valve 380 on fuel supply line 372, when this solenoid valve 380 only is driven in low frequency range at rotation compression member 4B, promptly rotate when being driven in the little zone of the pressure reduction of the head pressure of compression member 4B and suction pressure, become connected state, and this fuel supply line 372 is used for oil is fed to oil circuit 360, so when pressing chamber 43 injection oil are limited at the low frequency driving of rotation compression member 4B and hang down differential pressure, thus, can suppress to be stored in the consumption of the oil 8 of seal container 1, can high efficiency improve cooling effectiveness simultaneously.
And, in the present embodiment, exemplify the oil 8 that is stored in the high pressure in the seal container 1 is injected the structure of pressing chamber 43, but be not limited thereto, also can adopt the outer direct high pressure of the slave～oil of middle pressure to be injected into the structure of pressing chamber 43.Particularly, as shown in figure 14, can in refrigerating circuit 1200 ', adopt such structure: between the discharge side of closed rotary compressor 100B ' and condenser 1110 ', insert and oil is separated oil separator 1160 recovery, that return closed rotary compressor 100B ' from refrigeration agent, connect oil separator 1160 and described oil circuit 360 with fuel supply line 372 ', the part of the oil of oil separator 1160 recovery is offered oil circuit 360.At this moment, mode of execution with above-mentioned in the fuel supply line 372 ' is identical, and solenoid valve 380 ' is set, only when the rotation compression member 4B of closed rotary compressor 100B ' is driven in low frequency range, solenoid valve 380 ' becomes connected state, and described oil circuit 360 is supplied with oil.And, because fuel supply line 372 ' is closed by solenoid valve 380 ' sometimes, so, be preferably in the pipe that except that fuel supply line 372 ', is provided for returning oil between oil separator 1160 and the closed rotary compressor 100B ' in addition for the oil that oil separator 1160 is reclaimed stably turns back to closed rotary compressor 100B '.In addition, because be maintained at high pressure from the oil of oil separator 1160 guiding, so preferably adopt capillary tube 1170 decompression member such as (can be expansion valve) be set between oil separator 1160 and solenoid valve 380 ', adjust the pressure of oil in decompression after, supply to the structure of oil circuit 360.
In addition, in the present embodiment, exemplified closed rotary compressor 100B, but be not limited thereto, also can in closed rotary compressor, use the present invention certainly with 2 cylinders with 1 cylinder 41.
Claims (5)
1. hermetic type compressor, the rotation compression member of accommodating electrical components and being driven by described electrical components in seal container is characterized in that, comprising:
Fuel supply line, it is used for supplying with oil;
Oil circuit, it is connected with described fuel supply line, when the pressing chamber in the cylinder that constitutes described rotation compression member sucks refrigeration agent, described oil is injected in the described pressing chamber;
Solenoid valve, it is arranged on the described fuel supply line, is communicated with/disconnects according to the driver frequency of described rotation compression member.
2. hermetic type compressor according to claim 1 is characterized in that,
When the low load capacity zone of described rotation compression member, described solenoid valve becomes connected state.
3. hermetic type compressor according to claim 1 is characterized in that,
Described oil is stored in the described seal container, and described oil supplies to described oil circuit by described fuel supply line.
4. hermetic type compressor according to claim 1 is characterized in that,
Described fuel supply line is connected to the refrigerant circuit with oil separator, and described fuel supply line is connected with described oil separator, and described oil separator will be directed to described oil circuit by described fuel supply line from the oil of refrigerant-recovery.
5. hermetic type compressor according to claim 4 is characterized in that,
Have and be arranged on decompression member between described oil separator and the described solenoid valve, that the oil of supplying with from described oil separator is reduced pressure.
Applications Claiming Priority (9)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005-076664 | 2005-03-17 | ||
| JP2005076664A JP4854209B2 (en) | 2005-03-17 | 2005-03-17 | Hermetic compressor |
| JP2005076664 | 2005-03-17 | ||
| JP2005101232A JP4845409B2 (en) | 2005-03-31 | 2005-03-31 | Hermetic compressor |
| JP2005101233 | 2005-03-31 | ||
| JP2005-101232 | 2005-03-31 | ||
| JP2005101232 | 2005-03-31 | ||
| JP2005101233A JP2006283583A (en) | 2005-03-31 | 2005-03-31 | Hermetic compressor |
| JP2005-101233 | 2005-03-31 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006100574938A Division CN1834462B (en) | 2005-03-17 | 2006-03-17 | Hermetically sealed compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101354037A CN101354037A (en) | 2009-01-28 |
| CN101354037B true CN101354037B (en) | 2011-04-13 |
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Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008102118746A Active CN101354037B (en) | 2005-03-17 | 2006-03-17 | Hermetic compressor |
| CN2006100574938A Active CN1834462B (en) | 2005-03-17 | 2006-03-17 | Hermetically sealed compressor |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006100574938A Active CN1834462B (en) | 2005-03-17 | 2006-03-17 | Hermetically sealed compressor |
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| Country | Link |
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| JP (1) | JP4854209B2 (en) |
| CN (2) | CN101354037B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6015055B2 (en) * | 2012-03-27 | 2016-10-26 | 株式会社富士通ゼネラル | Rotary compressor |
| CN105402130B (en) * | 2015-11-20 | 2018-08-07 | 珠海格力电器股份有限公司 | Compressor slip sheet backpressure structure, compressor and air conditioner |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4968223A (en) * | 1988-02-04 | 1990-11-06 | Empresa Brasiliera de Compressores | Gas and oil cooling system for a hermetic compressor |
| US5545021A (en) * | 1993-12-21 | 1996-08-13 | Matsushita Electric Industrial Co., Ltd. | Hermetically sealed rotary compressor having an oil supply capillary passage |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06167287A (en) * | 1992-12-01 | 1994-06-14 | Hitachi Ltd | Rotary compressor |
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2005
- 2005-03-17 JP JP2005076664A patent/JP4854209B2/en active Active
-
2006
- 2006-03-17 CN CN2008102118746A patent/CN101354037B/en active Active
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4968223A (en) * | 1988-02-04 | 1990-11-06 | Empresa Brasiliera de Compressores | Gas and oil cooling system for a hermetic compressor |
| US5545021A (en) * | 1993-12-21 | 1996-08-13 | Matsushita Electric Industrial Co., Ltd. | Hermetically sealed rotary compressor having an oil supply capillary passage |
Non-Patent Citations (2)
| Title |
|---|
| JP平7-293470A 1995.11.07 |
| JP平8-114189A 1996.05.07 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1834462A (en) | 2006-09-20 |
| CN101354037A (en) | 2009-01-28 |
| CN1834462B (en) | 2010-11-10 |
| JP2006257971A (en) | 2006-09-28 |
| JP4854209B2 (en) | 2012-01-18 |
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Application publication date: 20090128 Assignee: Shenyang CATIC electromechanical SANYO refrigeration equipment Co., Ltd. Assignor: Sanyo Electric Co., Ltd. Contract record no.: 2017990000464 Denomination of invention: Closed compressor Granted publication date: 20110413 License type: Common License Record date: 20171127 |