CN1250877C - Enclosed compressor and freezer using such compressor - Google Patents
Enclosed compressor and freezer using such compressor Download PDFInfo
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- CN1250877C CN1250877C CN 03101402 CN03101402A CN1250877C CN 1250877 C CN1250877 C CN 1250877C CN 03101402 CN03101402 CN 03101402 CN 03101402 A CN03101402 A CN 03101402A CN 1250877 C CN1250877 C CN 1250877C
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Abstract
The invention provides a hermetically sealed compressor or a refrigerating apparatus capable of using hydrocarbon refrigerant and with high reliability. The hermetically sealed compressor comprises: a sealed container; an electric motor portion and a cylinder housed in the sealed container; a suction pipe penetrating the sealed container and connected to the cylinder so as to intake working fluid flowing therein; a piston disposed in the cylinder to compress the working fluid; a discharge pipe discharging the working fluid from the cylinder penetrating the sealed container; a means for adjusting pressure of a space inside the sealed container to be higher than pressure in the suction pipe and lower than pressure in the discharge pipe.
Description
Technical field
The present invention relates to a kind of hermetic type compressor that uses the hydrocarbon refrigeration agent as the refrigeration agent of refrigeration cycle, and the refrigerating plant that is provided with the refrigerator of the refrigeration cycle with this hermetic type compressor and air conditioner etc.
Background technique
In the existing compressor that in seal container, has a rolling piston, to be used to be divided into the blade in the hyperbaric chamber that refrigerant gas is drawn into the low pressure chamber in the cylinder chamber and the refrigerant gas that sucks is compressed, be contacted with the periphery of cylinder (rolling piston), make the cylinder revolution, blade is being contacted with to-and-fro motion repeatedly under the state of cylinder.In such compressor, the refrigerant gas after the compression is discharged to the space in the seal container for the moment.This refrigerant gas be set under the condensing temperature of refrigeration cycle saturation pressure promptly with discharge the approaching pressure of gas pressure.
On the other hand, in recent years in order to suppress global warming, developed and do not used the chlorofluorocarbon that is called as freon etc. as the refrigeration cycle of refrigeration agent with use freezing, the cold storage plant of this refrigeration cycle, this freon is difficult to decompose, and is considered to produce ozonosphere destroy.Refrigeration agent as the candidate of such defluorinate Leonization can list propane (R290) and isobutane hydrocarbon refrigeration agents such as (R600a).
These hydrocarbon refrigeration agents are owing to having combustibility as its character, so that breaks out when using in a large number, explodes is dangerous higher.In order to reduce this danger, preferably reduce the refrigeration agent use amount of equipment as much as possible.In addition, these refrigeration agents are dissolved in the many more character of volume of the cooling medium increase in the oil when high more owing to have atmosphere pressures when lubricant oil, so, generally be made as in higher (for example with the discharge gas pressure certain degree of compressor) pressure, cylinder and each all-in-one-piece rolling piston type rotary compressor of blade for the pressure in the seal container of the compressor that accumulates lubricant oil, need more refrigeration agent, use the refrigeration agent existing problems of such kind.
In such cylinder and each all-in-one-piece rolling piston compressor of blade, for blade is pressed to cylinder, by the elastic force of the spring that blade is applied elastic force towards the cylinder direction with supply to the pressure of the lubricant oil that has added high pressure in the container of the chamber of accommodating blade, the time the be everlasting back side of the blade when the cylinder side is seen add high pressure.Even compressor with high speed rotary, makes the inertial force of blade increase, can prevent that also the blade front end from leaving from cylinder.In addition, in compressor as described above, the cylinder inboard becomes the pressure with seal container internal pressure same degree.
In this occasion, the suction chamber that refrigeration agent compresses to comprising, that form by cylinder peripheral part and cylinder inner wall and the space of pressing chamber to sucking, promptly the fuel feeding of start chamber is outdoor to the indoor fuel feeding that carries out of this start from start.Specifically, since cylinder inboard for high pressure (with the discharge gas pressure of compressor be the pressure of same degree), so the lubricant oil (refrigerator oil) that supplies to the cylinder inboard bleeds by the gap between the slide part of cylinder and its bearing components under the effect of the differential pressure of cylinder inboard and working room.That is, the lubricant oil that is stored in the seal container that has added high pressure is from being in the part of the start chamber under the low suction pressure of pressure, and the micro-gap that promptly constitutes suction chamber flow in the cylinder, carries out the sealing of the each several part in the cylinder and lubricated.
Reduce refrigeration agent in hope and make in the seal container occasion at the meltage of lubricant oil for low pressure (with the pressure of the gas inhalating pressure same degree of compressor), the cylinder inboard is a low pressure, and the cylinder inside pressure likens to and is the pressure in the pressing chamber in the cylinder outside low (identical substantially with suction chamber).Therefore, in such formation, be difficult to from the cylinder inboard fully by the differential pressure of side direction pressing chamber, suction chamber in cylinder fuel feeding fully.
The pressure in the space in the seal container is set at the fuel feeding technology of suction chamber of the rolling piston type rotary compressor of the pressure littler than the head pressure of refrigeration agent, for example is recorded in Japanese kokai publication hei 6-213183 communique (prior art).Wherein, a side is set towards the inside opening of the inhalation part part of compression unit, the oily capillary tube that the other end court lodges in the oily split shed of seal container bottom.According to this formation, betide by the driving that is accompanied by compressor near the capillary end that sucks part negative pressure produce with seal container in pressure difference, by this differential pressure by capillary tube to sucking the part fuel feeding.
Above-mentioned prior art is not considered scheme suitable in the system that the rotating speed that makes compressor corresponding to freezing load changes.Its reason below is described.
That is, when the rotating speed that makes compressor changed, the air displacement of unit time changed, and sucked the change in flow of gas refrigerant.At this moment, the negative pressure of utilizing in above-mentioned prior art can be thought substantially square proportional with the flow velocity that sucks gas refrigerant.Supply to also square proportional with the flow velocity that sucks gas refrigerant substantially of oil mass that sucks part by capillary tube.
On the other hand, identical as pressure condition, the pressure difference of the unit time that lists then, promptly with irrelevant from the rotating speed of the pressure difference of the pressure difference of pressure difference, suction chamber and the seal container of relevant suction chamber of the leakage of start chamber and pressing chamber and pressing chamber and seal container and compressor, identical respectively, so delivery volume and the compressor rotary speed of the unit time of the lubricant oil in the slide part gap of sealing start chamber are irrelevant, and be certain substantially and abundant.
Yet when considering the refrigeration cycle of the reality of using compressor, along with the increase of the rotating speed of compressor, the refrigerating capacity of refrigeration cycle increases, so, the temperature difference increase of condensing temperature and evaporating temperature.Therefore, the head pressure of compressor and the pressure difference of suction pressure also increase, so, the leakage rate that is caused by the pressure difference in the pressure of start chamber and the space in the seal container is in the direction of increase, but the increase of the circulating mass of refrigerant that the increase of compressor rotary speed brings makes the absolute leak amount less, and leakage rate is little to the influence of circulating mass of refrigerant relatively.
That is, when considering to be applicable to the occasion of actual refrigeration cycle, can think that also the change of rotating speed of relative compressor changes little for the delivery volume of the unit time of the needed lubricant oil of sliding parts that seals the start chamber.
According to above-mentioned research as can be known, for above-mentioned prior art, the quantitative changeization of the lubricant oil of supplying with along with the increase and decrease of the rotating speed of compressor is bigger, so, can think the Performance And Reliability that has damaged compressor.Yet,, do not take in for this problem.That is, in above-mentioned prior art, reckon without corresponding to rotating speed and suitably regulate fuel feeding to the pressing chamber inboard.
For example, as make fuel delivery corresponding with a certain rotating speed of compressor, then when fuel delivery deficiency with than the revolution of its low speed the time, fuel delivery is excessive during high speed rotary.As set the delivery volume of lubricant oil corresponding to the rotating speed side of low speed, then along with rotating speed increases, it is too much that the delivery volume of lubricant oil becomes.When setting the delivery volume of lubricant oil corresponding to high speed rotating speed side, the delivery volume under the low rotation speed area became low.
The fuel delivery deficiency makes the sealing deficiency of start chamber, and the leakage rate of gas refrigerant increases, and the volumetric efficiency of compressor descends, and simultaneously, produces friction, the wearing and tearing of the direct contact generation of slide part, the reliability decrease of compressor.When fuel delivery is excessive, suck gas by the oil heating higher than the temperature that sucks gas, specific volume increases, and reduces volumetric efficiency.
In addition, as described above, remain the fuel feeding of the start chamber that the cylinder of compressor inwall of high pressure and cylinder and blade constitute in the seal container, undertaken by the oil of cylinder inboard is bled by the gap of cylinder slide part by the inboard differential pressure of cylinder with the start chamber.For this reason, to the fuel delivery of start chamber with changing by the high pressure of operating conditions decision and the differential pressure of start chamber pressure or the gap size of slide part.In addition, the lower limit of the gap size of slide part is restricted because of the restriction of the surface roughness of parts and machining accuracy etc., so, can not be controlled to oil mass to the required irreducible minimum that becomes performance the best.
For this reason, when friction, when wearing and tearing that hope prevents above-mentioned member, exceed the indoor needed oil mass of seal compression and exceedingly supply with a large amount of oil, suck gas by bleeding to the indoor a large amount of oil mass heating of start, specific volume is increased, reduce volumetric efficiency, add the gas refrigerant of hot press method, have the problem that whole adiabatic efficiency is descended by the oil of a large amount of high temperature.
In addition, as make in the seal container and to be lower pressure, then need to increase seal distance to the leakage paths of indoor sealing of start and slip surface fuel feeding.Like this, device is maximized, simultaneously, can not carry out the inflow of the lubricant oil that causes by differential pressure fully, have the reliability problems that is difficult to guarantee the cylinder slip surface from the gap.
Summary of the invention
The object of the present invention is to provide a kind of high hermetic type compressor or refrigerating plant of reliability that uses the hydrocarbon refrigeration agent.
In order to achieve the above object, compressor have seal container, be contained in motor part in this seal container and cylinder, the above-mentioned seal container of perforation be connected to above-mentioned cylinder and make above-mentioned working fluid be drawn into through inside this cylinder suction pipe, be disposed at the piston that in the above-mentioned cylinder above-mentioned working fluid compressed, connect that above-mentioned seal container is discharged the discharge tube of above-mentioned working fluid, the pressure of the above-mentioned suction pipe of pressure ratio inboard that makes the space in the above-mentioned seal container is high and the device regulated than the pressure lowland in the above-mentioned discharge tube from above-mentioned cylinder.
In addition, in order to achieve the above object, refrigerating plant has closed-type compressor, condenser, vaporizer, reaches refrigerant pipe; This closed-type compressor has seal container, is contained in the interior motor part of this seal container and cylinder, suction pipe, piston, discharge tube, reaches exhaust port; This suction pipe connects above-mentioned seal container, is connected to above-mentioned cylinder, and makes above-mentioned working fluid be drawn into this cylinder through inside; This cylinder configuration is turned round with the turning axle of above-mentioned motor in above-mentioned cylinder with being connected, and above-mentioned working fluid is compressed; This discharge tube connects above-mentioned seal container from above-mentioned cylinder, discharges above-mentioned working fluid; This exhaust port is communicated with this discharge tube, and the above-mentioned working fluid in the above-mentioned cylinder is flowed out; This refrigerant pipe makes above-mentioned working fluid be passed to above-mentioned condenser from above-mentioned discharge tube, makes above-mentioned working fluid be passed to above-mentioned suction pipe from above-mentioned vaporizer; Wherein, the pressure in the space in the above-mentioned seal container is adjusted to any the pressure of the above-mentioned working fluid from above-mentioned suction pipe to above-mentioned exhaust port.
Description of drawings
Fig. 1 is the profile diagram that constitutes substantially that the closed type rotary compressor of first embodiment of the invention is shown.
Fig. 2 is the A-A cross-section profile among Fig. 1.
Fig. 3 is the profile diagram of structure that the pressure regulator of compressor shown in Figure 1 is shown.
Fig. 4 is the profile diagram of formation of another example that the pressure regulator of compressor shown in Figure 1 is shown.
Fig. 5 is the figure that variation changed of the relative cylinder of the pressure angle of revolution in pressure and the pressing chamber that illustrates in the container of compressor shown in Figure 1.
Fig. 6 is the schematic representation that the formation of that the second embodiment of the present invention relates to, as to have the compressor of setting the pressure in the seal container high and lower than head pressure than suction pressure refrigeration cycle is shown.
Fig. 7 is the figure that constitutes substantially that the air conditioner of the refrigeration cycle of using Fig. 6 is shown.
Fig. 8 is the sectional view that the formation that the pressure in the seal container of the compressor of third embodiment of the invention is regulated is shown.
Fig. 9 is the figure of the allocation position of explanation intercommunicating pore shown in Figure 8.
Figure 10 is the figure of the allocation position of explanation intercommunicating pore shown in Figure 8.
Figure 11 illustrates the present invention's macrostructural profile diagram of another embodiment's compressor again.
Figure 12 illustrates the present invention's macrostructural profile diagram of another embodiment's compressor again.
Figure 13 is the figure that variation changed of the relative cylinder of the pressure angle of revolution in pressure and the pressing chamber that illustrates in the container of compressor shown in Figure 12.
Figure 14 illustrates the present invention macrostructural profile diagram of another embodiment's compressor and the schematic representation of the formation of the refrigeration cycle that has been connected this compressor again.
Figure 15 is the macrostructural profile diagram that the refrigerator of the refrigeration cycle of using Figure 14 is shown.
Figure 16 is the figure that variation changed of the relative cylinder of the pressure angle of revolution in pressure and the pressing chamber that illustrates in the container of compressor shown in Figure 14.
Embodiment
Below, according to Fig. 1-Figure 16 embodiments of the invention are described.
(embodiment 1)
Fig. 1 illustrates the horizontal arrangement type compressor 110 that is used for refrigeration cycle, has compression mechanical part and motor part in its seal container 6.In the present embodiment, compressor is a single cylinder, by the refrigeration agent of 8 compressions of rotating piston in cylinder 1 as the working fluid of refrigeration cycle.
The motor part of this compressor has by hot embedding etc. and is fixed in the stator 7 in the seal container 6 and is installed on live axle 4 and at the inboard rotating rotor 5 of stator 7.
In addition, compressor section is connected with the live axle 4 of above-mentioned motor part, is made the piston (cylinder) 8 that is disposed in the cylinder 1 along cylinder inner peripheral surface 1a revolution and back and forth be activated by the revolution of this live axle 4.In the present embodiment, the piston 8 that forms the inboard of columnar cylinder 1 substantially has the 8a of cylinder portion of general cylindrical shape of piston 8 and the tabular blade part 8b that extends to form from barrel surface and the 8a of the cylinder portion one of the 8a of this cylinder portion.Embedding the eccentric part 4a that is located at cylinder 1 counterpart of live axle 4 interior week of the 8a of cylinder portion.The 8a of cylinder portion can constitute pivotally around the eccentric part 4a of live axle 4.
As shown in Figure 2, in the outside of the cylindric inner peripheral surface 1a of cylinder 1, be provided with have with the central shaft of this 1a substantially parallel central shaft the hole 1b of portion cylindraceous and make its part be communicated to cylinder inner peripheral surface 1a.In addition, the opposition side (more lateral) with the central shaft of cylinder 1 of being at the 1b of relative opening portion has similarly and is set as the hole 1c of portion cylindraceous communicatively with the 1b of hole portion.Blade part 8b inserts and accommodates the space that the 1b of hole portion is linked to each other with the 1c of hole portion and forms.At the 1b of hole portion, sandwich blade part 8b ground assembling and contact slide member 9 slidably at the inner face of the tabular planar surface portion of blade part 8b and the 1b of hole portion.
In the both sides of cylinder 1, dispose the bearing components of the such supporting driving shaft of main bearing 2 and supplementary bearing 3 with the peripheral members of cylinder 1 with being connected, connect the live axle 4 of cylinder 1 by the 2a of bearing portion, 3a supporting.For this reason, the central shaft of the inner peripheral surface 1a of the central shaft of live axle 4 and cylinder 1 as one man is provided with.
According to above formation, make live axle 4 revolutions by the revolution of the rotor 5 of motor part, thereby cylinder 1 in, piston 8 is turned round driving, cylinder inner peripheral surface 1a and piston 8 slips are turned round (or keeping micro-gap), carry out relative movement.In addition, as described above, blade part 8b is configured in the 1b of hole portion that is provided with communicatively with cylinder 1 and the inside of the 1c of hole portion, the central shaft that relative eccentric part 4a is carried out in the motion of the piston 8 that is produced by the revolution along with live axle 4 to to-and-fro motion.When carrying out this to-and-fro motion, make the reciprocating action of slide member 9 relative blade part 8b and revolution start and its 8b of supporting blade portion accordingly.Carrying out rotation motion around the inner peripheral surface 1a of cylinder 1 carries out reciprocally swinging on one side on one side to make piston 8 by its motion.
Sealing between blade part 8b and the 1b of hole portion, the 1c (vane room in the space promptly reciprocal as these blade parts 8b, that revolution is moved) keeps by the space of inserting slide member 9, occupy between 1b of hole portion and the blade part 8b.Like this, form as the pressing chamber 10 of confined space and suction chamber 11, along with the revolution of live axle 4 makes its volume increase and decrease repeatedly as the suction space of refrigeration agent by cylinder 1, piston 8, main bearing 2, supplementary bearing 3, slide member 9.
The refrigeration agent of refrigeration cycle inside is drawn in the seal container 6 from the suction pipe 12 that connects seal container 6.This suction pipe 12 is connected with the compression mechanical part of inboard outside seal container 6, is connected with the refrigerant pipe of external container.Be compressed after entering into suction chamber 11 via suction passage 13.Refrigeration agent after the compression is discharged to by supplementary bearing 3 and the discharge cover 14 discharge chamber 3c that form by the not shown expulsion valve that is formed at this bearing from the tap hole 3b that is formed at supplementary bearing 3.After this, be discharged to outside the seal container 6 from the discharge tube 15 that connects seal container 6.
The suction of these refrigeration agents, discharge are carried out along with the swing of piston 8.That is, the suction of refrigeration agent by make piston 8 around live axle 4 revolution (swing) once, the volume of increase suction chamber 11 carries out.Then, by making piston 8 around live axle 4 revolutions (swing), make by the inner peripheral surface 1a of the periphery of piston 8, cylinder, main bearing 2, supplementary bearing 3, and the volume reducing of the confined space separated of slide member 9, so, the pressing chamber 10 that the refrigeration agent in this space is compressed become.By reducing the volume of pressing chamber 10, make indoor refrigeration agent be compressed and discharge from tap hole 3b.
In the present embodiment, make piston 8 swings of the 8a of cylinder portion and the blade part 8b of integrally formed piston 8.The occasion that forms respectively at cylinder portion and blade part need be pressed to cylinder portion guaranteeing the sealing of pressing chamber with blade by high pressure, so, make the pressure in the container higher in the past, with high pressure the lubricant oil in the oil groove 16 are supplied to vane room etc.And in the present embodiment that constitutes like this, do not have such necessity, can make in the seal container 6 of compressor to be relatively low pressure.
Discharge chamber 3c by changing the stream basal area, work as silencing apparatus, simultaneously, also as working by the direction transformation separating oil of stream and the oil separator of gas refrigerant.Also can in discharging the chamber, put into wire netting or steel wool, make to be easier to catch oil droplet.Separate and lodge in the oil of discharging indoor recess and turn back to the seal container bottom by capillary tube 60.
The following describes the formation of fuel feeding of the lubricant oil of present embodiment.
In the present embodiment, exert pressure and carry out at lubricant oil by the motion of blade part 8b to the fuel feeding of compressing mechanism and live axle.As described above, the front end of blade part 8b moves in the 1c of hole portion, and the oscillating motion of piston 8 and blade part 8b constitute uninterruptedly.
The 1c of hole portion is immersed in the oil groove 16 in the seal container 6, and the 1c of hole portion is positioned under the pasta.Side's side of the 1c of this hole portion is communicated to suction port 17 and the oil that sucks flows to the oily passage of the 1c of hole portion side.In addition, the oily channel connection that passes through of the opposing party's side and the oily exhaust port 18 and the oil of discharging.Direction towards the 1c of hole portion sucks lubricant oil 16 from suction port 17 by the motion of blade part 8b.In addition, the lubricant oil in the 1c of hole portion is expressed into the direction of fuel supply line 19 from exhaust port 18 through oily passage.At this moment, suction port 17 and exhaust port 18 subtract aisle spare ground in the direction from oil groove 16 to the 1c of hole portion, direction from the 1c of hole portion to fuel supply line 19 respectively and form, and play the effect of so-called fluid diode.
For this reason, make the lubricant oil in the 1c of hole portion be difficult for fluidly forming, be easy to fluidly form towards fuel supply line 19 directions towards oil groove 16 directions by the motion of blade part 8b.Lubricant oil flow into the shaft end side of live axle 4 from fuel supply line 19.Then, flow into bearing portion (eccentric part) in the 8a of piston rotor portion from being formed on spiral chute 20a by the part of the live axle 4 of supplementary bearing 3 supporting.Then, flow into the spiral chute 20b that is formed at live axle 4 surfaces by the part of main bearing 2 supporting.
In addition, the lubricant oil that flow into cylinder portion 8a inboard flows to the motor part side to the surface of the bearing portion in live axle 4 and the 8a of cylinder portion with being lubricated.Like this, lubricant oil is supplied to the rotating part of live axle 4 and piston 8, cylinder 1.Then, the lubricant oil that supplies to spiral chute 20b flows out in the seal container 6 from the end of the spiral chute 20b of main bearing 2 sides, and rotor 5, the stator 7 of motor part cooled off, and turns back to oil groove 16.
In addition, the refrigerant gas in the cylinder 1 flow into the inboard of the 8a of cylinder portion sometimes from the piston 8 and the gap of cylinder 1, flow into the 8a of cylinder portion of piston and the slip surface of eccentric part 4a then.At this moment, as having gas at slip surface, then 8a of cylinder portion and live axle 4 are easy to produce adhesion, so, need make the gas runaway.
In the present embodiment, in live axle 4, form air hole 4b, the 4c that is communicated to the end of live axle 4 from eccentric part 4a.Lubricant oil on the slip surface and refrigerant gas are by the rotating action of centrifugal force of live axle 4, be separated into less relatively refrigerant gas of proportion and bigger lubricant oil, refrigerant gas flow into the private side of live axle 4, flows out in the seal container 6 by vent.
In addition, except the refrigerant gas from vent 4b, 4c, the gas refrigerant that is spilt by the gap between the parts that constitute pressing chamber makes the pressure in the seal container 6 rise than the pressure height in the suction pipe 12.
Below, illustrate present embodiment to the indoor fuel feeding of start.In the present embodiment, be provided with the device that the pressure that makes in the suction pipe 12 and the pressure in the seal container 6 produce the difference of the size of stipulating.That is, in the present embodiment, be provided with the device that the pressure in the interior space of the suction pressure that makes the start chamber that is made of cylinder inside wall and piston (cylinder and blade) and container creates a difference.
Fig. 3 is the tectonic maps that makes the defferential valve of the device that creates a difference between suction pipe internal pressure and seal container internal pressure of the present invention.In the figure, valve 51 is the inaccessible valve of being located at the opening ground configuration of discharging cover 14.This valve 51 is located in the supplementary bearing 3, is located in the valve chamber 50 that is communicated with above-mentioned opening portion.In addition, valve 51 applies pushing force by the helical spring 52 of the retainer in valve chamber 50 54 location towards the direction of inaccessible opening.
In addition, be communicated with valve chamber 50 form communication channel 53 interiorly with suction pipe 12.Valve chamber 50 makes the basal area of flow of refrigerant direction than the setting of communication channel the earth, and the influence ground that reduces the flowing velocity of the refrigeration agent in the suction pipe 12 constitutes.
The pushing force that helical spring 52 produces is Fk+Fs (Fk: spring force as shown in the figure like that, Fs: the size power that is added to valve 51 by the gas in the valve chamber 50), if affacted the power Fg of the opening portion (area A) that is communicated with the passage of discharging cover 14 and threshold chamber 50 by the pressure P i in the seal container 6 big unlike Fk+Fs, then valve 51 keeps closed condition.As Fg＞Fk+Fs, then valve 51 is open, and in the connection seal container 6 and in the valve chamber 50, therefore, is communicated with in suction pipe 12 and the seal container 6.
When the pressure in the seal container 6 surpassed the value Pi of regulation, valve 51 was opened, and was communicated with in the suction pipe 12 low with opening pressure, and can make the pressure in the container once more is Pi.Like this, the compressor of present embodiment in seal container 6 pressure and the pressure in the suction pipe 12 between set pressure differential, the pressure in the seal container is adjusted to higher but than the low pressure of the pressure in the discharge tube (discharge gas pressure) than the pressure in the suction pipe pressure of gas (suck).
Fig. 4 is the sectional view that another structure of defferential valve is shown.This figure is the modified example that is used to form the device of pressure shown in Figure 3, and example shown in Figure 3 uses helical spring 52 and valve 51, and example shown in Figure 4 use leaf spring 51 '.In the example of Fig. 4, also by leaf spring in leaf spring 51 ' the apply pushing force of Fk+Fs, during the power Fg that produces as the pressure P i in the seal container 6＞Fk+Fs, leaf spring is pushed and reaches valve chamber 50 sides, by valve chamber 50 and communication channel 53 will suction pipe 12 in 6 interior connections of seal container.
Like this, in the present embodiment, the seal container internal pressure becomes the pressure that exceeds the centre of specified value than suction pipe internal pressure by the effect of above-mentioned control valve unit.
In the above-described embodiments, connect valve chamber 50 and the seal container 6 interior passages that form, be provided with and regulate in the valve chamber 50 and the device of the gas flow between in the container.As these devices, be arranged on the valves 51,51 of action in the valve chamber 50 '.In addition, the extent of pressure can according to for example to valve apply the helical spring 52 of elastic force and leaf spring 51 ' intensity, rigidity and connection be formed in the valve chamber 50 of discharging cover 14 with seal container 6 in the area A of above-mentioned passage in space be adjusted to size arbitrarily.In addition, space in the container arrives the shape in the path that the gas refrigerant of suction pipe flows, also by at the medial compartment that storage gas is set on the path, basal area change etc. is suitably selected, can be corresponding with the specification of matching requirements and pressure etc.
The seal container pressure relevant when the oil that Fig. 5 illustrates the cylinder inboard bleeds to the start chamber by the gap of cylinder slide part and the pressure difference of start chamber with its delivery volume.As pay close attention to the gas that certain sucks in a flash, then rotary compressor carries out suction stroke at the crank rev, carries out compression stroke and discharges stroke at the rev of remainder.When the angle of revolution that makes crank 360 ° when beginning the crank up angle of (suction stroke end) for compression stroke, angle of revolution 0 ° of expression suction stroke begins, and the 720 ° of expressions in angle of revolution are discharged stroke and finished.
Solid line illustrates the pressure of suction chamber and pressing chamber, is shown in dotted line seal container pressure, and oblique line portion illustrates its pressure difference.The condition here is the condition of the refrigerator of refrigerant R134a, suction pressure 101kPa, head pressure 837kPa with compressor.In Fig. 5 of present embodiment (a), the relative suction pressure of seal container pressure that for example becomes intermediate pressure forms the differential pressure ground that exceeds 100kPa approximately and sets defferential valve.The Fig. 5 (b) that becomes the conventional example of high-pressure closed vessel compares with Fig. 5 (a), and the area of the oblique line portion of demonstration differential pressure is bigger.At high-pressure closed vessel, exceedingly supply with a large amount of oil, compressor performance (volumetric efficiency, overall adiabatic efficiency) descends.In the present embodiment, by suitably setting differential pressure, may be adjusted to the oil mass favourable to performance.That is, in seal container, become substantially in the existing rotary compressor of row pressure power, before pressing chamber becomes head pressure, from the 8a of cylinder portion to the indoor supply refrigerator oil of start.Yet, when becoming suitable intermediate pressure in the seal container, when the pressure ratio intermediate pressure in the pressing chamber is high, reduce to the supply of the refrigerator oil of pressing chamber from the 8a of cylinder portion, on the contrary, refrigerator oil may move to the 8a of cylinder portion.
As described above, specification according to device remains the poor arbitrarily of setting with suction pressure and seal container internal pressure, the variation to the fuel delivery of start chamber that reduces that the rotating speed change of compressor causes, the change that the variation by compressor rotary speed of the oil mass of discharging from pressing chamber with gas refrigerant causes also is suppressed.Therefore, should also irrespectively in the unit time, be roughly necessarily by the oil that the discharge chamber 3c that works as oil separator separates with compressor rotary speed.
Actual refrigerator generally keeps the temperature inside the box operation definitely as far as possible, and environment temperature also is a room temperature, so the pressure condition of the compressor of running seldom produces big variation.Therefore, will by discharge oil that chamber 3c separated turn back in the discharge chamber 3c at capillary tube 60 two ends of seal container 6 bottoms with seal container 6 in pressure difference can not produce big variation yet, so, the amount of restriction of the capillary tube 60 by suitably setting present embodiment can irrespectively will the oil mass identical substantially with the oil mass that supplies to the start chamber turn back to the bottom of seal container 6 with the operating conditionss such as rotating speed of compressor.Therefore, can alleviate because the adhesion that causes to the fuel delivery deficiency of the delivery volume of the oil of start chamber and the shortage of oil of accumulating to the bottom at seal container that the imbalance of the oil amount of returning of the bottom of seal container causes, slide part, damage etc. make the degree that the reliability of compressor, refrigerator suffers damage.
Like this, by the pressure in suction pressure and the seal container being remained the value of regulation, can make the change of the fuel delivery of the unit time that supplies to the start chamber along with the variation of compressor rotary speed is the optimum state, in addition, delivery volume is reduced, near required minimum flow, so, the decline of past can be suppressed because of the Performance And Reliability of oversupply lubricant oil generation.
In addition, by suppressing change, also reduce with the change of gas refrigerant from the unit time of the oil of pressing chamber discharge to start chamber fuel delivery., also reduce from the change of the recirculating oil quantity of oil separator unit time, the design that is used for the throttling of oil return becomes easy for this reason.
In addition,, the seal container internal pressure adds the pressure that obtains after the regulation differential pressure owing to being made as in suction pressure, so, can reduce the meltage of refrigeration agent to lubricant oil, therefore, favourable to the refrigeration cycle of using the hydrocarbon refrigeration agent.
(embodiment 2)
Below, according to Fig. 6, Fig. 7 another embodiment of the present invention is described.Present embodiment is regulated defferential valve according to the information of refrigeration cycle, forms the seal container internal pressure to operating conditions the best of refrigeration cycle.The essential structure of compressor is identical with Fig. 1, Fig. 2 shown in first embodiment, so same section adopts same-sign, omits its explanation.
In Fig. 6, compressor 110a have be used to regulate in the suction pipe 12 with seal container 6 in the pressure-regulating valve 70 and the pressure adjustment pipe 71 of pressure difference, when pressure-regulating valve 70 is opened, be communicated with suction pipe 12 and seal container 6, when pressure-regulating valve 70 is closed, inaccessible suction pipe 12 and seal container 6.
The separation of oil that is contained in the gas refrigerant that is compressed is different with embodiment 1, is undertaken by oil separator 73.Oil separator 73 has the container that intake channel 73a, gas outlet pipe 73b, oily outlet pipe 73c have been installed, and the gas refrigerant that flows into from intake channel 73a is rotated in the container, by density difference from gas separation oil.Gas refrigerant flows out from gas outlet pipe 73b, when oil accumulates established amount in container, by the effect of float 75 needle-valve 74 is opened, and flows out from oily outlet pipe 73c, and the return tube 72 of the seal container 6 by being installed on compressor turns back in the seal container 6.
Switch the operation of cold air and heating installation four-way threshold 76, outdoor heat converter 77, indoor heat converter 78, expansion valve 79, and connecting pipings 80a, the 80b refrigeration cycle ground that constitutes cold air and heating installation operation be connected.Fan 81,82 is respectively outdoor and indoor fan.
Fig. 7 is the schematic representation of the air conditioner of the refrigeration cycle of use Fig. 6.In the inboard of building 150 indoor set 112 is set, at arranged outside outdoor unit 113.Dress indoor heat converter 78, fan 82 etc. in indoor set 112.In addition, dress compressor 110a, outdoor heat converter 77, fan 81 etc. in outdoor unit 113.
Temperature sensor 120, indoor heat converter temperature transducer 121, outer temperature degree sensor 122, outdoor heat converter temperature transducer 123, compressor surface temperature transducer 124, and seal container pressure sensor 125 be used to detect the temperature and pressure of each one.In addition, to indoor side control gear 130a, outdoor control gear 130b, and the rotating speed of fan and compressor the frequency variator 131,132,133 controlling and drive as revolution speed control device distinguish the control of the each several part of correspondence.
Control gear 130a, 130b detect setting room temperature from remote controller 140, set the instruction of air quantity, according to the deviation of temperature sensor 120 etc., send instruction to valve 76,79, frequency variator 131～133.
By with heat exchanger 77, the temperature of temperature transducer that becomes the heat exchanger of vaporizer in 78 is assumed to the saturation temperature of refrigeration agent, obtain the saturation pressure corresponding with it, deduct the pressure loss of pipe arrangement from it from heat exchanger to the compressor suction pipe, thereby the suction pressure when obtaining compressor operating in addition, by with heat exchanger 77, the temperature of temperature transducer that becomes the heat exchanger of vaporizer in 78 is assumed to the saturation temperature of refrigeration agent, obtain the saturation pressure corresponding with it, the pressure loss of the pipe arrangement till adding from the compressor discharge tube to heat exchanger, thereby the head pressure of trying to achieve.Because the pipe arrangement pressure loss is relevant with gas density, flow velocity etc., so also can be used as the function of saturation pressure, compressor rotary speed etc.These calculating are undertaken by control gear.
The air conditioner of frequency variator drive-type is corresponding to the heat load operation relevant with the air temperature difference of indoor and outdoor, so compared with the occasion of the equable refrigerator of the temperature inside the box and environment temperature, the head pressure of compressor and suction pressure variation are greatly.Therefore, be used to seal the head pressure start chamber relevant and leak needed oil mass with the bigger change of operating conditions generation with the pressure difference of suction pressure.The sealing of start chamber keeps used oil to equate substantially with the seal container internal pressure in that cylinder is inboard, so the oil of cylinder inboard bleeds by the gap of cylinder slide part under the differential pressure effect of cylinder inboard and start chamber and carries out.
In the present embodiment, so, by suitably regulating the seal container internal pressure, can carry out fuel feeding to the favourable amount of performance corresponding to operating conditions.In addition, " pressure difference of seal container internal pressure and the suction pressure " conduct that to for example should set in advance " head pressure and suction pressure poor " and the function or the data of " compressor rotary speed " store, control gear 130a, 130b is as explained above according to heat-exchanger temperature sensor 121, the suction pressure that 123 checkout value etc. calculates, head pressure, and the rotating speed of compressor sends instruction to the pressure-regulating valve 70 as the compression adjustment device, regulate action, make it become the interior pressure of desired seal container (detecting) by pressure transducer 125.
These storage devices are installed in control gear 130a, the 130b and can pull down and change, also can use and different condition, storage device and control gear that machine is corresponding.In addition, the data of storage also can be used as above-mentioned function storage as the combination storage of each data, use the actuating quantity of detected predetermined data calculating pressure regulating device in control gear, and it is sent as instruction.
According to above formation and effect, can suitably regulate with the different fuel delivery ground of operating conditions and supply with to the start chamber, reduce the change of the fuel delivery that the change of the rotating speed of compressor causes, suppress the decline of the reliability that the deficiency of decreased performance that excessive fuel feeding causes and fuel delivery causes.
(embodiment 3)
Below, with reference to Fig. 8, Fig. 9, Figure 10 and Fig. 1,2 explanation another embodiment of the present invention.
Present embodiment is characterised in that the certain interval in the rev process of compressor is provided with the pressing chamber of connection compression unit and the hole in the seal container, replaces Fig. 3 of first embodiment, defferential valve shown in Figure 4.The essential structure of compressor is identical with Fig. 1, Fig. 2 shown in first embodiment, omits its explanation.
A kind of such example is disclosed in Japanese kokai publication sho 55-107093 communique, this example makes the perforate that is communicated with in compressor section and the seal container by setting in scroll compressor, to form the intermediate pressure of suction pressure and head pressure in the seal container, different with the purpose of the rotary compressor of present embodiment with effect.In the scroll compressor of above-mentioned communique, be intermediate pressure by making the seal container internal pressure, act on and act on the rightabout pushing force of axial force of rotation wrap component.In addition, in the scroll compressor of above-mentioned communique, connect the bottom and the suction pipe of seal container by capillary tube, by the differential pressure of seal container internal pressure (intermediate pressure) and suction pressure from suction pipe to the compressor section fuel feeding.On the other hand, in the rotary compressor of present embodiment, by cylinder slide part gap to start chamber fuel feeding.
In Fig. 8, hole 100 is opened in the end plate of the main bearing side of compression unit, for seal container in the hole of spatial communication.Hole 100 is communicated with pressing chamber by 540 ° (180 °) in angle of revolution and its angle of revolution nearby, in other interval, by cylinder end face obturation.This hole 100 is provided with respectively with the tap hole of refrigerant gas, can be only compression section constantly arbitrarily, the time be communicated with start in the cylinder indoor with seal container in the space.
Pressing chamber pressure P c is (Vc/Vs) k times of (Vs: get rid of volume of suction pressure Ps, Vs: compression chamber volume, k: adiabatic index), for example in the occasion of R134a, compressor suction pressure as refrigerator is 101kPa, and then the pressing chamber pressure of 540 ° of angles of revolution is about 230kPa (with reference to Fig. 5).Therefore, only in the angle of revolution 540 ° and its angle of revolution nearby be communicated with in pressing chamber with seal container in the space, thereby at the pressing chamber pressure of 540 ° and its angle of revolution nearby during with seal container internal pressure generation differential pressure in the angle of revolution, gas is come by intercommunicating pore 100, under steady state, the seal container internal pressure can be remained on pressure than the high approximately 130kPa of suction pressure.Like this, similarly to Example 1, can be by differential pressure to start chamber fuel feeding.
Below, the allocation position of intercommunicating pore 100 is described with reference to Fig. 9, Figure 10.Illustrate that in the angle of revolution 495 °～585 ° scope is communicated with the occasion in space in pressing chamber and the seal container here.The oblique line portion of Fig. 9 (a) illustrates the zone of the suction chamber (inhalation process) that is formed by 0 °～360 ° in the angle of revolution scope and the zone of the pressing chamber (compression, discharge operation) that 360 °～495 ° scope forms in the angle of revolution.This zone comprise by week in the cylinder, with (piston rotor portion outer radius-offset) as 495 ° of piston rotor portion peripheries of locating in circle (circumferential section shown by dashed lines), angle of revolution of radius, and the zone that surrounds of other track of piston constitute.The oblique line portion of Fig. 9 (b) is illustrated in the zone of the pressing chamber that the scope of 495 °～585 ° of angles of revolution forms.It is circle (circumferential section shown in broken lines), and the zone that surrounds such as blade part of radius that this zone comprises by week in the cylinder, the 495 ° of piston rotor portion peripheries located in angle of revolution, with (piston rotor portion outer radius-offset).In addition, the oblique line portion of Fig. 9 (c) is illustrated in the zone of the pressing chamber that the scope of angle of revolution 585 °～720 ° (0 °) forms.This zone comprises by week in the cylinder, the 585 ° of piston rotor portion peripheries located in angle of revolution, and the zone that surrounds such as blade part.
For only 495 °～585 ° interval is communicated with space in pressing chamber and the seal container in the angle of revolution, can be in the oblique line portion of Fig. 9 (b) intercommunicating pore is not set with the main bearing side board of (a) and oblique line portion (c) crossing part.This zone is illustrated by oblique line in Figure 10.
This zone comprises the zone that is surrounded by the 495 ° of piston rotor portion peripheries located in track, angle of revolution etc. of cylinder blade joint that with (piston rotor portion outer radius-offset) are 495 °～540 ° of circle (circumferential section shown by dashed lines), the angles of revolution of radius.Being equivalent to (piston rotor portion outer radius-offset) is that the inboard suitable main bearing end plate portion of the circle of radius is not communicated with pressing chamber often, so, also can intercommunicating pore 100 be set as shown in the figure like that in the oblique line portion that comprises this part.In addition, the shape in hole 100 and Fig. 3,4 similarly at random have shapes such as length and basal area corresponding to the size of specification of obtaining and pressure.
In the present embodiment, compression section in the pressure rising, be set on the interior sidewall surface of cylinder by the opening of will be only at the appointed time, being communicated with the passage in pressing chamber and the container between the angle of revolution, can make container inner pressure big or small arbitrarily, or set lowlyer than head pressure than suction pressure height.By same constituting, from the position arbitrarily of the piston rotor of the operation that is drawn into compression, discharges of refrigeration agent, at interval, be communicated with the space that start is indoor and seal container is interior, make the refrigerant gas circulation, thereby can will be set in the seal container from being drawn into the pressure arbitrarily of discharge.Like this, according to the desired pressure difference that suction pressure, head pressure produce, can suitably regulate amount to the indoor supplying lubricating oil of start.
In the present embodiment, the mechanism as the seal container internal pressure of compressor being remained intermediate pressure is provided with intercommunicating pore at the main bearing end plate, so, compare with embodiment 1 defferential valve, can realize cost degradation.
(embodiment 4)
Below, with reference to Figure 11 another embodiment of the present invention is described.
Figure 11 is the profile diagram of the compressor of fourth embodiment of the invention, and compressor is a rolling piston type double cylinders rotary compressor.In embodiment 3 embodiment, use the compressor of rolling piston to constitute as cylinder portion and blade part all-in-one-piece, the difference of these embodiments and present embodiment is that the piston in the cylinder is made of the parts that separate with blade part cylinder portion.
Figure 11 illustrates the transverse compressor 110b that is used for refrigeration cycle, has compression mechanical part and motor part in this seal container 6.In the present embodiment, compressor is a twin-tub, by rotating drum piston 27a, b in cylinder 22a, 22b the refrigeration agent of refrigeration cycle is compressed.Compression mechanical part is connected with the live axle 4 of motor part, is made piston (cylinder) 27a, the b that are disposed in the cylinder along inner peripheral surface 22c, d revolution by the revolution of this live axle 4, is subjected to reciprocal driving, and this point is same as the previously described embodiments.
In addition, in the present embodiment, also the interior all sides with drum piston 27a, b are embedded into eccentric part 26a, the b that is located at the part corresponding with cylinder on the live axle 4.Drum piston 27a, b can constitute pivotally around the eccentric part 4a of live axle 4.
As shown in figure 11, blade part 28a, b accommodate and are assembled in cylinder 22a, the b outside and its vane room that is provided with communicatively, from applying elastic force with drum piston 27a, b opposition side by each spring 29a, b, are pressed to cylinder.In addition, same with the foregoing description, dispose the bearing components of the such supporting driving shaft of main bearing 24 and supplementary bearing 25 in the both sides and the peripheral members of cylinder of cylinder with being connected, connect live axle 26 in cylinder 22a, the b by the 24a of bearing portion, 25a supporting.For this reason, central shaft and the inner peripheral surface 22c cylindraceous of cylinder 22a, b, the central shaft of d of live axle 26 as one man are provided with, revolution along with live axle 4, drum piston 27a, the b and the inner peripheral surface slip that are subjected to turning round driving in cylinder 1 are turned round (or keeping micro-gap), carry out relative movement, simultaneously, blade part 28a, b move back and forth keeping the state that is pushed to cylinder towards radially (live axle 26 directions) of the cylinder that is provided with communicatively with cylinder.When carrying out this to-and-fro motion, blade slides being pushed on the surface of contact of cylinder relatively moving radially of cylinder.Like this, constitute the suction chamber that forms as the suction space of the pressing chamber of confined space and refrigeration agent,, its volume is increased and decreased repeatedly along with the revolution of live axle by these.
In the formation of present embodiment, in having the refrigeration cycle of pressurized gas, carry out the circuit refrigeration agent and be drawn in the seal container 6 from the suction pipe 12 that connects seal container 6, be compressed enter into the suction chamber of cylinder 22a, 22b via suction passage after.Refrigeration agent after the compression is discharged to discharge chamber 32a, the b that is formed by supplementary bearing 25 and discharge cover 31a, b from tap hole 30a, the b that is formed at supplementary bearing 25 by the expulsion valve that is formed at this bearing.Be discharged to the refrigeration agent of discharging chamber 32a and flow out to discharge chamber 32b, afterwards, be discharged to outside the seal container 6 from the discharge tube 15 that connects seal container 6 by being communicated with the passage of discharging chamber 32a, b.Be provided with below the discharge tube 15 of discharging chamber 32b and be contained in the space that the lubricant oil in the discharging refrigerant gas accumulates, the lubricant oil in this space of accumulating is by flowing out to oil groove 16 with the capillary tube 60 of being located at the open communication of discharging 32b bottom, chamber.
The formation of the fuel feeding of the lubricant oil of present embodiment is also similarly carried out with the foregoing description, by the reciprocating action of blade part 28a, b the lubricant oil that is drawn in the vane room from through oil hole 33 is exerted pressure, and supplies to the front end of live axle 26 by passage 19.At this moment, suction port 33 reduces aisle spare ground towards the direction from the 1c of hole portion to fuel supply line 19 and forms, and plays the effect of so-called fluid diode.In addition, the bearing portion (eccentric part) of spiral chute 20 in piston rotor portion and the bearing portion supplying lubricating oil of major and minor bearing 24,25 by the part that is formed at live axle 26, simultaneously, by the passage of being located in the axle gas of the bearing portion that results from eccentric part is gone out towards the motor part effluent, this point is also same as the previously described embodiments.
In addition, except refrigerant gas, also make the pressure in the seal container 6 rise than the pressure height in the suction pipe 12 by the gas refrigerant that spills by the gap between the parts that constitute pressing chamber from above-mentioned vent.Present embodiment also is provided with the device of the difference of the pressure generation prescribed level in the pressure that makes in the suction pipe 12 and the seal container 6.Also can obtain equally in the present embodiment by the action effect that is used for producing arbitrarily pressure (suction chamber internal pressure) and the device of the difference of seal container 6 internal pressures in the suction pipe 38 that explanation in the above-described embodiments is set.
In the present embodiment, as prior art, the 6 interior pressure occasion lowlands identical with the pressure in the discharge tube are set than making seal container to make container inner pressure.So, past is owing to applied higher relatively pressure, delivered to vane room lubricant oil, blade is pressed to cylinder, so, to produce local bigger face pressure between cylinder and blade part and produce adhesion, wearing and tearing, damage in order to be suppressed at, need be to a large amount of lubricant oil of start chamber supply, and in the present embodiment, because it is relatively low blade to be pressed to the power of cylinder, so the amount of the lubricant oil of supply also can reduce.
The delivery volume of the lubricated needed lubricant oil of the sealing of start chamber and cylinder/blade for example can suitably be regulated according to the area of the intensity of the spring that valve is applied elastic force and communication channel, shape etc. as described above.In addition, the pressure in the container is because the occasion of the compressor of comparable prior art is low, so, also can reduce the amount of dissolving in the occasion of using the hydrocarbon refrigeration agent, reduce volume of the cooling medium, so, can improve refrigeration cycle and have the Security and the reliability of its freezing, aircondition.
(embodiment 5)
Below, with reference to Figure 12～13 explanations another embodiment more of the present invention.
The compressor of Figure 12 is the compressor with two compression units that used oscillating-piston, relates to the compression unit a side has been subjected to the so-called two stage compressor that compression unit that refrigerant compressed supplies to the opposing party compresses once more.Figure 13 is the figure that the difference of the indoor pressure of space in the seal container that changes along with the rotary position of piston and start is shown.Device as regulating the pressure in the seal container can use the control valve unit of Fig. 3, Fig. 4, the intercommunicating pore of Fig. 8 etc.
The compressor 110c of present embodiment has low pressure (rudimentary suction pressure), the middle pressure (rudimentary head pressure, senior suction pressure) higher than low pressure, three pressure levels that high high pressure (senior head pressure) is pressed in the ratio centre substantially.In the present embodiment, compressor seal container internal pressure is not one that adopts in these three pressure, but can advantageously at random set pressure in the seal container to performance.
In Figure 12, the gas refrigerant in the refrigeration cycle is drawn in the seal container 6 from first suction pipe 36 that connects seal container 6, first cylinder 1 that constitutes first compression unit ' in carry out first time and compress.Gas refrigerant after the compression flows out to first discharge tube 37 from tap hole 30b by discharging chamber 32b.That is, carry out first order compression by first compression unit.After this refrigeration agent is being discharged to outside the seal container 6 from first expulsion valve 37 that connects seal container 6.
Be discharged to for the moment seal container 6 outer gas refrigerants and cool off by surrounding atmosphere, be drawn into once more in the seal container 6 by second suction pipe 39 that connects seal container 6 then by interstage cooler 38.The gas refrigerant that is drawn into suction pipe 39 is at second cylinder 1 that constitutes second level compression unit, and " the compression second time is carried out in inside, flows out to second discharge tube 40 from tap hole 30a by discharging chamber 32a.That is, carry out second level compression.Refrigeration agent is after this outside discharge tube 40 is discharged to seal container 6.
At this moment, the seal container internal pressure by the device of the setting seal container internal pressure that in embodiment 1,2, describes in detail remain than first cylinder 1 ' the high but pressure lower of suction pressure than the head pressure of refrigeration agent.In the occasion of Fig. 3, control valve unit shown in Figure 4, connect in first suction pipe 36 and in the seal container 6 by valve.In addition, in the occasion of intercommunicating pore shown in Figure 8, be communicated with by the interior regulation of the start chamber of the compression unit of the rudimentary side (first order) that forms such as first cylinder 1 ' wait and seal container and be provided with intervally.
In the present embodiment, in order to realize high performance, make the compression work of rudimentary side and senior side equally set the air displacement of rudimentary compression unit and advanced compression unit, and make that the compression ratio of rudimentary side is identical substantially with the compression ratio of senior side under the authorized pressure condition.
Figure 13 illustrates the variation with the crank up angle of the compression unit of the compression unit of the first order (rudimentary) of two stage compressor and the second level (senior) of start room pressure and seal container internal pressure.Solid line illustrates the pressure of suction chamber and pressing chamber, is shown in dotted line seal container pressure, and oblique line illustrates its pressure difference.Its condition is that refrigeration agent 134a, rudimentary side suck the condition of the refrigerator of pressure 101kPa, senior side head pressure 837kPa with compressor.At this moment, rudimentary side is identical substantially with the pressure ratio of senior side, and it is 291kPa that rudimentary side head pressure and senior side suck pressure.
As prior art, pressure as the seal container shown in Figure 13 (b), in the occasion of using senior suction pressure, for rudimentary compression unit, the pressure difference (oblique line portion) of senior suction pressure 291kPa and start chamber (suction chamber, pressing chamber) pressure becomes driving force, the gap of the oil of cylinder inboard by the cylinder slide part supply to first cylinder 1 ', carry out the sealing of this start chamber.For the oil of the start chamber of advanced compression unit sealing usefulness, the oil of discharging with gas refrigerant from rudimentary compression unit supplies to the start chamber by the suction pipe of advanced compression unit.
At this moment, at Figure 13 (b), supply exceeds the needed excessive oil of least limit, by the oily heating and cooling agent of a large amount of high temperature, in the volumetric efficiency of compressor, the occasion that overall adiabatic efficiency descends, in the present embodiment, such shown in Figure 13 (a), by the seal container internal pressure being set at the value lower than senior suction pressure, can make the fuel delivery optimization, improve performance.In this occasion, even the rotating speed of compressor increase and decrease also can reduce to supply to the change of amount of the lubricant oil of first cylinder 1 ' interior, suppress the decrease in efficiency of the compressor that oversupply lubricant oil causes, improve performance.In addition, the lubricant oil that flows into second cylinder is undertaken by supplying to first cylinder and being contained in the lubricant oil that circulates in the refrigerant gas.The amount that correspondence is fed to this second cylinder also takes in, adjustable settings lead to first cylinder 1 ' suction pipe 36 in the interior pressure of pressure and seal container 6 poor.
On the contrary, in the occasion of Figure 13 (b),, the seal container internal pressure can be set than senior suction pressure height when when the fuel feeding of start chamber is not enough.
(embodiment 6)
Below, with reference to Figure 14～15 explanations another embodiment more of the present invention.
Compressor shown in Figure 14 is for using the rotary compressor of above-mentioned oscillating-piston.But, in the present embodiment, in circuit way, have the COMM communication of valve, changeable compression of being undertaken by a pressing chamber and the compression of being undertaken by two pressing chambers.The compressor of present embodiment also has the device of regulating in the seal container, has between the pressure in pressure and the space in the container in the suction pipe of start chamber the generation formation of the pressure difference of value arbitrarily.As the controlling device of this pressure, also can use any device that illustrates in the foregoing description.
In Figure 14, the constituting substantially of the refrigeration cycle of present embodiment comprise compressor 110d with two cylinders, condenser 62, refrigerating chamber with vaporizer 64a, cold storage room with vaporizer 64b and connect and make the refrigeration agent refrigerant pipe that circulates of portion within it.In addition, dispose the blowing fan 66,67,68 that is used to blow respectively at condenser 62 and vaporizer 64.Like this, in the present embodiment, flow out from discharge tube 40, deliver to condenser 62, afterwards, be diverted to refrigerating chamber vaporizer 64a and cold storage room vaporizer 64b by the refrigeration agent after the compressor 110d compression.The refrigeration agent that flows out from these vaporizers flow into compressor once more by refrigerant pipe and compresses, and constitutes circulation.
The compressor 110d of present embodiment have two cylinders 1 ', 1 ", they have the suction pipe 36,39 and 37,40 that is used to suck with discharging refrigerant gas respectively.Can will deliver to second cylinder 1 by these cylinders and " compress promptly so-called secondary compression once more by the refrigerant gas after first cylinder 1 ' compression.
For this reason, by with first cylinder 1 ' the refrigeration agent that forms of the refrigerant pipe that is connected of discharge tube 37 mobile be divided into two directions, one square tube is crossed the discharge tube 40 that connects second cylinder and the refrigerant path of condenser 62 is connected by refrigerant pipe with one-way valve 61b, and the opposing party is connecting cold storage room that refrigerating chamber uses with the vaporizer 64b and second cylinder 1 " the refrigerant path of suction pipe 39 be connected by refrigerant pipe by interstage cooler 38.In addition, between this branching portion and interstage cooler 38 configuration to the mobile solenoid valve 65b that regulates of refrigeration agent.
In addition, be connected with condenser 62, be branched off into two pipes, by capillary tube 63a, b one side is connected to the vaporizer 64a that refrigerating chamber is used respectively, the opposing party is connected to cold storage room vaporizer 64b from the refrigerant pipe of the flow of refrigerant of condenser.That is, refrigerating chamber is configured to capillary tube 63b between the branching portion and each vaporizer of refrigerant pipe with capillary tube 63a, cold storage room, with for example setting of refrigerant pipe of the flow of refrigerant that flows out from vaporizer with carrying out heat exchange with being in contact with one another.The solenoid valve 65a of can regulate flow of refrigerant is set between above-mentioned branching portion and cold storage room are with capillary tube 63b in addition.
In addition, make from refrigerating chamber with the refrigeration agent of vaporizer 64a outflow flow into first cylinder 1 ' suction pipe 36 ground by refrigerant pipe refrigerant path is set, simultaneously, the refrigerant path that flow into the suction pipe 39 of second cylinder at the refrigeration agent that flows out with vaporizer 64b from cold storage room is provided with refrigerant pipe by non return valve 61a inflow place branch.
In such formation, regulate flowing of refrigeration agent by the action of one-way valve 61a, b, solenoid valve 65a, b, can with use first, second cylinder 1 of compressor ', 1 " being compressed in above-mentioned secondary compressed action and between the compression arranged side by side that two cylinders compress refrigeration agent side by side, switching of refrigeration agent.Promptly, the flow path of the refrigeration agent that changeable one-tenth is such, in the flow path of this refrigeration agent, from condenser 62 diverted flow, flow into suction pipe 36 at refrigerating chamber with the refrigeration agent that vaporizer 64a has carried out evaporation, simultaneously, be compressed at first cylinder with the vaporized refrigeration agent of vaporizer 65a by cold storage room, flow into the suction pipe 39 of second cylinder after converging with the refrigeration agent that flows out from discharge tube 37, after the compression, flow out from discharge tube 40; In addition, the flow path of the refrigeration agent that also changeable one-tenth is such, in the flow path of this refrigeration agent, from condenser 62 flow out, refrigerating chamber with vaporizer 64a carried out the refrigeration agent that evaporates respectively branch flow into the suction pipe 36,39 of first, second cylinder, after compression, flow out from discharge tube 37,40.
In Figure 15, the refrigerator of present embodiment has refrigeration cycle shown in Figure 14, has formation matched with it.Refrigerator body 200 portion within it is provided with a plurality of storerooms, from begin to have cold storage room 203A, vegetable compartment 203B, refrigerating chamber 202A, the 202B of secondary up and down.A plurality of vaporizers are set in refrigerator 200, at higher level's refrigerating chamber 202A rear portion configuration refrigerating chamber vaporizer 64a, at vegetable compartment 203B rear portion configuration cold storage room vaporizer 64b, configuration is used for the fan 67,68 to vaporizer air supply stream above these vaporizers.
By the revolution of fan in these evaporator cools air have by different paths supply to storeroom, from turning back to the circulating path of vaporizer after storeroom flows out.That is, have by refrigerating chamber and become the circulating path of the cold airflow that turns back to vaporizer 64a from subordinate refrigerating chamber 202B rear portion with vaporizer 64a cooling, after flowing out in refrigerating chamber 202A, the B by fan 67 and by vaporizer 64b cooling, supply to cold storage room 203A, cooled off and flow into vegetable compartment 203B behind the cold storage room 203A, become the circulating path that container rear in the vegetable compartment turns back to the cold airflow of vaporizer 64b by fan 68.In order to separate these cold airflows, configuration has the partition wall of thermoinsulation material between refrigerating chamber 202A and vegetable compartment 203B.
In addition, at the rear configuration compressor 110d of the refrigerating chamber of the bottom of the back side of refrigerator 200, condenser 62, condenser with fan 66, and solenoid valve 65a, b.In addition, the refrigerator of present embodiment has the control gear 231 of the action that is used to regulate refrigeration cycle shown in Figure 14.This control gear accept to detect the temperature in refrigerating chamber temperature transducer 218, detect the temperature of refrigerating chamber and vegetable compartment temperature transducer 219, and detect the output of temperature transducer 220,221 of the temperature of vaporizer, send instruction with fan 66, vaporizer with the frequency variator 232,233,234,235 of the rotating speed of fan 67,68 to the motor of regulating compressor 110d changeably, condenser, the refrigerating capacity in the regulating box.In addition, send the instruction that its action is regulated, switch flowing of refrigeration agent, switch secondary compression, the operation of compression side by side of compressor 110d to solenoid valve 65a, b.In addition, instruct the operation of the defrosting heater 216,217 that each vaporizer uses, heating fumigators defrosts.
In the present embodiment, by the operation ground setting operation plate 236 that the user at random regulates refrigerator 200, can send operating instruction to control gear 231 at the Men Shangke of cold storage room 203A by the operation of this plate 236.In addition, corresponding with the operation of the flowing of cooling operation in each storeroom of refrigerator 200 and the refrigeration agent that switches, compressor 110d, undertaken by the action of solenoid valve 65a, 65b.
For example, the temperature in the refrigerating chamber, cold storage room all than the predefined high occasion of temperature when beginning to cool down operation, is judged the storeroom that needs the cooling both sides by control gear 231, makes solenoid valve 65a, b move open position ground together and instructs.In this occasion, from the refrigeration agent branch of condenser 62, flow into refrigerating chamber respectively with vaporizer 64a, cold storage room vaporizer 64b, refrigerating chamber and cold storage room are cooled off.From refrigerating chamber with the refrigeration agent of vaporizer 64a from suction pipe 36 flow into first cylinder 1 ', be compressed the back and discharge from discharge tube 37.
After converging with the refrigeration agent of vaporizer 64b and refrigeration agent from cold storage room, flow into second cylinder 1 from suction pipe 39 and " be compressed from discharge tube 37.That is, by refrigerating chamber with the refrigeration agent of vaporizer 64a by first cylinder 1 ' and second cylinder 1 " repeatedly compress.
Begin the high occasion of temperature at refrigerating chamber only than predefined cooling, or according to instructing the occasion of cooling operation of refrigerating chamber forcibly from the instruction of operation panel 236, the operation of only cooling off refrigerating chamber individually.In this occasion, solenoid valve 65a closes, and the opening action ground that carries out solenoid valve 65b sends instruction from control gear.Like this, only flow into refrigerating chamber vaporizer 64a from the refrigeration agent of condenser 62, the refrigeration agent that flows out from vaporizer 64a be branched off into first, second cylinder 1 ', 1 ", flow into from suction pipe 36,39, side by side compression.That is, compress side by side by each cylinder, discharge respectively, flow into condenser 62 after converging from the refrigeration agent of refrigerating chamber with vaporizer 64a, like this, the operation of compressing side by side.
In the present embodiment, the pressure in the seal container 6 also is adjusted to than the pressure height in the suction pipe of first cylinder, than the low pressure of the pressure in the discharge tube by the device of the pressure in the setting seal container that describes in detail in first, second embodiment.Pressure in the discharge tube can be the occasion of first cylinder, also can be the occasion of second cylinder, in the occasion of second cylinder, equates substantially with the saturation pressure of the refrigeration agent of condenser inlet.Present embodiment has the device that the pressure in the seal container is set at the intermediate value of these pressure.
In the occasion of Fig. 3, defferential valve shown in Figure 4, be connected by the differential pressure threshold with seal container 6 is interior in first suction pipe 36.In addition, in the occasion of intercommunicating pore shown in Figure 8, be provided with in interval the connection in the pressing chamber that forms by first cylinder 1 ' wait and the seal container of regulation.Like this, the pressure in the seal container 6 is with the compression of above-mentioned secondary with remain pressure than the high regulation of suction pressure of suction pipe 36 side by side during compression.
Occasion in the secondary compression, for the oil that separates by the discharge chamber 32b of first cylinder, 1 ' side, since be located at the opening below that is disposed at the discharge tube 37 of discharging chamber 32b and with the pressure difference at the two ends of being located at the capillary tube 60a that discharges the open communication in the 32b of chamber promptly discharge in the 32b of chamber with seal container 6 in pressure difference less, so, be not easy to turn back in the seal container 6, be stored in and discharge in the 32b of chamber, when excessively accumulating, along with refrigerant gas flows out by first discharge tube 37 together.
The oil that goes out from rudimentary compression unit (being subjected to first order compression with the refrigeration agent of vaporizer 64a from refrigerating chamber) first cylinder, 1 ' effluent supplies to the advanced compression unit with gas refrigerant and (for carrying out second cylinder 1 ") that the second level is compressed from refrigerating chamber with the refrigeration agent of vaporizer 64a, carries out the seal action of start chamber.The oil of discharging from this advanced compression unit separates with refrigerant gas in discharging chamber 32a with below being stored in container, by the more senior head pressure of high pressure and the differential pressure of the pressure in the seal container 6 turn back to seal container 6 inner bottom parts by capillary tube 60b.
For separation, discharge oil that chamber 32a, 32b separate by each and turn back to the interior bottom of seal container 6 by capillary tube 60a, 60b by the differential pressure of the pressure in head pressure and the seal container at the oil of the occasion of carrying out single stage compression side by side.
At this moment, in secondary compression and compression both sides' arranged side by side occasion, the oil that has been separated by discharge chamber 32a turns back in the seal container 6 by capillary tube 60b.Relevant to the rudimentary compression unit of the fuel delivery of start chamber and Figure 16 (a) that the recirculating oil quantity of discharge chamber 32a when compressing with secondary is relevant by the differential pressure shown in the oblique line portion.Being correlated with that the recirculating oil quantity of discharge chamber 32a during in addition, with single stage compression is relevant to the fuel delivery of start chamber and advanced compression unit (b) by the differential pressure shown in the oblique line portion.When secondary compression and single stage compression, the seal container internal pressure is all set to such an extent that exceed the pressure of regulation than suction pressure.Therefore, the differential pressure at recirculating oil quantity, capillary tube two ends of discharging chamber 32a equates substantially during with single stage compression when secondary compress, can be compressed and single stage compression by corresponding secondary by an amount of restriction.
In addition, before and after secondary compression and single stage compression are switched, owing to the seal container internal pressure can be remained certain pressure substantially, so, can prevent that the seal container internal pressure from changing the foaming that causes being dissolved in the refrigeration agent in the oil.
As described above, according to the present invention, can provide the closed-type compressor of high-performance high reliability that can corresponding hydrocarbon refrigeration agent.
Claims (10)
1. hermetic type compressor, have: seal container, be contained in motor part in this seal container, have in inside the piston that working fluid is compressed cylinder, connect above-mentioned seal container be connected to above-mentioned cylinder and with working fluid guide to this cylinder suction pipe, connect above-mentioned seal container from above-mentioned cylinder for discharging the discharge tube of above-mentioned working fluid, it is characterized in that: also have the high and adjusting portion that regulate than the pressure lowland in the above-mentioned discharge tube of the pressure that makes the above-mentioned suction pipe of the pressure ratio inboard in the above-mentioned seal container.
2. hermetic type compressor according to claim 1, wherein, when the pressure of the working fluid that the pressure ratio in above-mentioned seal container flows in above-mentioned suction pipe exceeds regulation big or small, above-mentioned adjusting portion action.
3. hermetic type compressor according to claim 1, wherein, have by above-mentioned cylinder, above-mentioned piston and start chamber that the end plate of their obturations is constituted, when the indoor authorized pressure of the above-mentioned start of the pressure ratio in the above-mentioned seal container is high, above-mentioned adjusting portion action.
4. hermetic type compressor according to claim 1, wherein, a plurality of above-mentioned cylinders are set, when the working fluid of discharging from a side cylinder was drawn into the opposing party's cylinder, above-mentioned adjusting portion was adjusted to the pressure in the space in the above-mentioned seal container between the pressure in a pressure in above-mentioned the opposing party's the discharge tube of cylinder and an above-mentioned side's the suction pipe of cylinder.
5. hermetic type compressor according to claim 1, wherein, above-mentioned adjusting portion has the interior passage of the space that is communicated with in the above-mentioned seal container and above-mentioned suction pipe and is configured to valve on this passage.
6. hermetic type compressor according to claim 3 wherein, has the passage and the opening portion of being located at above-mentioned start chamber and linking to each other with above-mentioned passage that are communicated with the space in the indoor and above-mentioned seal container of above-mentioned start.
7. hermetic type compressor according to claim 6, wherein, when carrying out compression section in above-mentioned start chamber, above-mentioned opening portion along with the revolution of piston to the indoor opening of above-mentioned start.
8. hermetic type compressor according to claim 1, wherein, be configured in the above-mentioned cylinder, have the above-mentioned piston with the cylinder of general cylindrical shape and tabular blade integratedly, be accompanied by the revolution of swing by above-mentioned motor, thereby compress above-mentioned working fluid.
9. refrigerating plant has: closed-type compressor, condenser, vaporizer, and refrigerant pipe; This closed-type compressor has seal container, be contained in the motor part in this seal container, the cylinder that has the piston that working fluid is compressed in inside, connect the suction pipe that above-mentioned seal container is connected to above-mentioned cylinder and working fluid is guided to above-mentioned cylinder, connect above-mentioned seal container and discharge the discharge tube of working fluid in the above-mentioned cylinder, and the high and adjusting portion that regulate than the pressure lowland in the above-mentioned discharge tube of the pressure of inboard that makes the above-mentioned suction pipe of pressure ratio in the above-mentioned seal container; This condenser makes the working fluid condensation of discharging by refrigerant pipe from above-mentioned discharge tube; This vaporizer makes liquid refrigerant flash to gas; This refrigerant pipe makes the working fluid that has carried out heat exchange in this vaporizer be passed to above-mentioned suction pipe; It is characterized in that: also have regulating mechanism, this regulating mechanism make the pressure in the above-mentioned discharge tube of pressure ratio in the seal container of above-mentioned hermetic type compressor low, than the pressure height in the above-mentioned suction pipe.
10. refrigerating plant according to claim 9, wherein, above-mentioned regulating mechanism is adjusted the pressure in the above-mentioned seal container according to the testing result of the temperature transducer of the working fluid temperature that detects above-mentioned condenser or above-mentioned vaporizer.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP000230/2002 | 2002-01-07 | ||
| JP2002000230A JP4013552B2 (en) | 2002-01-07 | 2002-01-07 | Hermetic compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1431402A CN1431402A (en) | 2003-07-23 |
| CN1250877C true CN1250877C (en) | 2006-04-12 |
Family
ID=19190461
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 03101402 Expired - Fee Related CN1250877C (en) | 2002-01-07 | 2003-01-07 | Enclosed compressor and freezer using such compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4013552B2 (en) |
| CN (1) | CN1250877C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104903660A (en) * | 2012-12-28 | 2015-09-09 | 大金工业株式会社 | Refrigeration device |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4797715B2 (en) * | 2006-03-09 | 2011-10-19 | ダイキン工業株式会社 | Refrigeration equipment |
| JP2007247562A (en) * | 2006-03-16 | 2007-09-27 | Denso Corp | Refrigerant compressor |
| JP5144897B2 (en) * | 2006-03-27 | 2013-02-13 | 三洋電機株式会社 | Refrigeration cycle equipment |
| CN103375407B (en) * | 2012-04-27 | 2016-04-27 | 比亚迪股份有限公司 | A kind of scroll compressor |
| CN105156154B (en) * | 2014-09-29 | 2018-12-04 | 摩尔动力(北京)技术股份有限公司 | Swing sliding equipment |
| CN106768566B (en) * | 2017-03-15 | 2023-05-05 | 广西大学 | Friction force measuring device for sliding vane and sliding chute of rolling piston compressor |
| DE102021201091A1 (en) * | 2021-02-05 | 2022-08-11 | Thyssenkrupp Ag | Compressors, in particular refrigerant compressors, refrigeration machines, and methods for producing a compressor |
-
2002
- 2002-01-07 JP JP2002000230A patent/JP4013552B2/en not_active Expired - Fee Related
-
2003
- 2003-01-07 CN CN 03101402 patent/CN1250877C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104903660A (en) * | 2012-12-28 | 2015-09-09 | 大金工业株式会社 | Refrigeration device |
| CN104903660B (en) * | 2012-12-28 | 2016-08-31 | 大金工业株式会社 | Refrigerating plant |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4013552B2 (en) | 2007-11-28 |
| JP2003201963A (en) | 2003-07-18 |
| CN1431402A (en) | 2003-07-23 |
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