CN203785327U - Refrigeration circulation device and air conditioner with same - Google Patents
Refrigeration circulation device and air conditioner with same Download PDFInfo
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- CN203785327U CN203785327U CN201420145201.6U CN201420145201U CN203785327U CN 203785327 U CN203785327 U CN 203785327U CN 201420145201 U CN201420145201 U CN 201420145201U CN 203785327 U CN203785327 U CN 203785327U
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- 230000004087 circulation Effects 0.000 title abstract description 11
- 238000005057 refrigeration Methods 0.000 title abstract 5
- 238000007710 freezing Methods 0.000 claims description 46
- 230000008014 freezing Effects 0.000 claims description 46
- 230000009183 running Effects 0.000 claims description 40
- 230000006835 compression Effects 0.000 claims description 12
- 238000007906 compression Methods 0.000 claims description 12
- 239000003921 oil Substances 0.000 abstract description 154
- 239000000446 fuel Substances 0.000 abstract description 22
- 238000012935 Averaging Methods 0.000 abstract 4
- 239000010721 machine oil Substances 0.000 abstract 1
- 230000000717 retained effect Effects 0.000 abstract 1
- 239000003507 refrigerant Substances 0.000 description 40
- 230000000694 effects Effects 0.000 description 8
- 239000007788 liquid Substances 0.000 description 8
- 238000001816 cooling Methods 0.000 description 7
- 238000007599 discharging Methods 0.000 description 7
- 238000012423 maintenance Methods 0.000 description 6
- 230000007812 deficiency Effects 0.000 description 5
- 238000010438 heat treatment Methods 0.000 description 5
- 238000004378 air conditioning Methods 0.000 description 4
- 230000005494 condensation Effects 0.000 description 4
- 238000009833 condensation Methods 0.000 description 4
- 238000011144 upstream manufacturing Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000000052 comparative effect Effects 0.000 description 2
- 238000009987 spinning Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 238000009355 double cropping Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 235000015927 pasta Nutrition 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Abstract
The utility model aims to provide a refrigeration circulation device and an air conditioner with the refrigeration circulation device. The refrigeration circulation device can eliminate non-uniformity of retained oil mass of multiple compressors and can ensure demanded fuel head in all compressors. A plurality of compressors (10 and 30) are arranged in parallel in a cryogen loop; the refrigeration circulation device (2) is characterized by comprising an oil averaging pipe (55) and a valve (55a); the compressors (10 and 30) are mutually connected through the oil averaging pipe (55) to enable the interior space of the compressor (10) to be communicated with that of the compressor (30) and to enable refrigerating machine oil to flow between the compressors (10 and 30); the valve (55a) is arranged in the oil averaging pipe (55) and used for opening or closing the oil averaging pipe (55).
Description
Technical field
The utility model relates to the freezing cycle device of multiple compressors parallel connection and has the air conditioner of this freezing cycle device.
Background technology
In the multicell multiple-connecting air conditioner of the ability more than having 10HP, be mostly multiple compressors in parallel in freeze cycle, each compressor turns round under same control.But, in each compressor, produce the difference of small operating condition, therefore, slightly different from the drag-out of the refrigerator oil of each compressor.Thus, the maintenance oil mass of each compressor is inhomogeneous, therefore, easily in a part of compressor, produces because of the not enough caused unfavorable condition of refrigerator oil.
In patent documentation 1, the freezing cycle device that discharge side at compressor disposes oil eliminator and couples together between by oil eliminator and the suction side of compressor with oil return pipe is disclosed.In this freezing cycle device, the refrigerator oil of discharging together with cold-producing medium from compressor is separated with cold-producing medium in oil eliminator, flows into the suction side pipe arrangement of compressor via oil return pipe, turns back to compressor together with the cold-producing medium having circulated in freeze cycle.
In addition, following air conditioner is disclosed in patent documentation 2: make the bottom tube connector that is installed on each compressor be increased to the fuel head (Japanese: レ ベ Le), with oil equalizing pipe (Japanese: oil equalizing pipe) top of the tube connector of two compressors is joined to one another in compressor.In this air conditioner, utilize the equal oil running of simultaneously carrying out with air conditioning running to regulate the fuel head in each compressor.
Prior art document
Patent documentation
Patent documentation 1: TOHKEMY 2004-293822 communique
Patent documentation 2: Japanese Patent Publication 6-40947 communique
Utility model content
Utility model is Yaoed the problem of Xie Decision
But, in the disclosed freezing cycle device of patent documentation 1, there are the following problems: the refrigerator oil of discharging from each compressor turns back in each compressor via oil eliminator, oil return pipe and suction side pipe arrangement, and therefore, the inhomogeneous of maintenance oil mass of eliminating each compressor needs the long period.In addition, there are the following problems: until cannot be by the inhomogeneous elimination of the maintenance oil mass producing in the compressor of halted state before starting next time.Particularly, (for example only carrying out in multiple compressors some, in two compressors, only have a compressor) running one-sided running after, multiple compressors, with after mutually different frequency run, is difficult to guarantee required fuel head in each compressor.
And, in the disclosed air conditioner of patent documentation 2, by oil equalizing pipe, the bottom of two compressors is joined to one another, therefore, when the fuel head of a compressor reduces, the fuel head of another compressor is also reduced to bottom sometimes.Thus, there are the following problems: cannot guarantee required fuel head in the two at two compressors, be easy to all produce at two compressors the unfavorable condition causing because of refrigerator oil deficiency.
The utility model is made at least one solution in problem as described above, and its object is to provide can be eliminated maintenance oil mass inhomogeneous of multiple compressors and can in each compressor, guarantee the freezing cycle device of required fuel head and have the air conditioner of this freezing cycle device.
For the means of dealing with problems
Freezing cycle device of the present utility model is the freezing cycle device with a plurality of compressors in parallel, it is characterized in that, this freezing cycle device comprises: oil equalizing pipe, it is joined to one another above-mentioned compressor and the inner space of above-mentioned compressor is communicated with, and refrigerator oil is circulated between above-mentioned compressor; Valve, it opens and closes above-mentioned oil equalizing pipe.
Preferably on the sidewall of above-mentioned compressor, be formed with the connector being connected with above-mentioned oil equalizing pipe, above-mentioned connector is located at than the top side's of compression mechanical part of above-mentioned compressor position.
Preferably when above-mentioned compressor all stops or above-mentioned compressor during each other with same frequency run, above-mentioned valve becomes out state, some when running only in above-mentioned compressor, or above-mentioned compressor is during with mutually different frequency run, and above-mentioned valve becomes the state of closing.
Air conditioner of the present utility model, is characterized in that, it comprises above-mentioned freezing cycle device.
The effect of utility model
Adopt the utility model, be provided with for making refrigerator oil at the oil equalizing pipe of compressor chamber circulation, therefore, can eliminate maintenance oil mass inhomogeneous of a plurality of compressors.In addition, adopt the utility model, be provided with the valve for oil equalizing pipe is opened and closed, therefore, can in each compressor, guarantee required fuel head.
Accompanying drawing explanation
Fig. 1 means the freezing cycle device 2 of embodiment 1 of the present utility model and has the refrigerant loop figure of schematic configuration of the air conditioner 1 of freezing cycle device 2.
Fig. 2 means the refrigerant loop figure as the refrigerant loop from evaporimeter to condenser of the major part structure of the freezing cycle device 2 of embodiment 1 of the present utility model.
Fig. 3 means the refrigerant loop figure as the major part structure of the freezing cycle device without oil equalizing pipe 55 and valve 55a of the comparative example of the freezing cycle device 2 of embodiment 1 of the present utility model.
Fig. 4 means the top view as the summary of the example of the connection structure of the oil equalizing pipe in the freezing cycle device with 3 above compressors of the variation of embodiment 1 of the present utility model.
Fig. 5 means the top view as the summary of the example of the connection structure of the oil equalizing pipe in the freezing cycle device with 3 above compressors of the variation of embodiment 1 of the present utility model.
Fig. 6 means the top view as the summary of the example of the connection structure of the oil equalizing pipe in the freezing cycle device with 3 above compressors of the variation of embodiment 1 of the present utility model.
The specific embodiment
Embodiment 1.
The freezing cycle device of embodiment 1 of the present utility model and the air conditioner with freezing cycle device are described.Fig. 1 means the freezing cycle device 2 of present embodiment and has the refrigerant loop figure of schematic configuration of the air conditioner 1 of freezing cycle device 2.In Fig. 1, mainly with thick line, represent the pipe arrangement for cold-producing medium circulation, mainly with fine rule, represent the pipe arrangement for refrigerator oil circulation.
First, use Fig. 1 to describe the overall structure of air conditioner 1 and freezing cycle device 2.As shown in Figure 1, air conditioner 1 has freezing cycle device 2.Freezing cycle device 2 has mainly, by refrigerant piping, compressor 10,30, cross valve 40, outdoor heat exchanger 50, expansion gear 60 and indoor heat exchanger 70 is in turn connected into the structure that ring-type forms.
In addition, air conditioner 1 has off-premises station 100 and indoor set 200.The fan 51 for off-premises station that off-premises station 100 has above-mentioned compressor 10,30, cross valve 40, outdoor heat exchanger 50 and expansion gear 60, air is blowed to outdoor heat exchanger 50.The used for indoor machine fan 71 that indoor set 200 has above-mentioned indoor heat exchanger 70, room air is blowed to indoor heat exchanger 70.In addition, in this example, expansion gear 60 is located in off-premises station 100, but expansion gear 60 also can be located in indoor set 200.In addition, in Fig. 1, only illustrate 1 indoor set 200, but air conditioner 1 also can have many indoor sets 200.Many indoor sets 200 have respectively the indoor heat exchanger 70 being connected in parallel to each other in refrigerant loop.
Compressor the 10, the 30th, sucks the gas refrigerant of low-temp low-pressure compress, and forms the cold-producing medium of HTHP and the fluid device of discharging.In the present embodiment, two compressors 10,30 are in parallel in refrigerant loop.In the back the details of compressor 10,30 is discussed.
Cross valve 40 is for switching refrigerant flow path.The in the situation that of cooling operation, (figure 1 illustrates the situation of cooling operation), 40 pairs of refrigerant flow paths of cross valve switch, so that the cold-producing medium of the HTHP of discharging from compressor 10,30 flows into outdoor heat exchanger 50, and the gas refrigerant of the low-temp low-pressure flowing out from indoor heat exchanger 70 is inhaled into compressor 10,30.On the other hand, in the situation that heating running, 40 pairs of refrigerant flow paths of cross valve switch, so that the cold-producing medium of the HTHP of discharging from compressor 10,30 flows into indoor heat exchanger 70, and the gas refrigerant of the low-temp low-pressure flowing out from outdoor heat exchanger 50 is inhaled into compressor 10,30.
Off-premises station with fan 51 for air being blowed to outdoor heat exchanger 50 by driving by motor the spinning movement producing.
Outdoor heat exchanger 50 is for to carrying out heat exchange between the mobile cold-producing medium of portion within it and the extraneous gas that blowed with fan 51 by off-premises station.Outdoor heat exchanger 50 as the condenser of condensation of refrigerant is played a role, plays a role as the evaporimeter that cold-producing medium is evaporated the in the situation that of cooling operation in the situation that heating running.
Expansion gear 60, for making the cold-producing medium after inflow expand and reduce pressure, forms the gas-liquid two-phase cold-producing medium of low-temp low-pressure and flows out.As expansion gear 60, use expansion valve, capillary etc.
Used for indoor machine fan 71 blows room air for the spinning movement by being produced by motor driving to indoor heat exchanger 70.
Indoor heat exchanger 70 is for to carrying out heat exchange between the mobile cold-producing medium of portion within it, the room air that blowed by used for indoor machine fan 71.Indoor heat exchanger 70 plays a role as the evaporimeter that cold-producing medium is evaporated in the situation of cooling operation, in the situation that heating running, as the condenser of condensation of refrigerant is played a role.
Fig. 2 means the refrigerant loop figure via compressor 10,30 refrigerant loops to condenser from evaporimeter as the major part structure of the freezing cycle device 2 of present embodiment.In Fig. 2, compressor 10,30 is shown to longitudinal section, the inscape beyond compressor 10,30 is shown with symbol or frame table.In addition, in Fig. 2, omitted the diagram of cross valve 40.For " evaporimeter " in Fig. 2, the in the situation that of cooling operation, for indoor heat exchanger 70, in the situation that heating running, be outdoor heat exchanger 50.In addition, for " condenser " in Fig. 2, the in the situation that of cooling operation, for outdoor heat exchanger 50, in the situation that heating running, be indoor heat exchanger 70.
As shown in Fig. 2 and Fig. 1 of having illustrated, two compressors 10,30 are in parallel in refrigerant loop.The suction side pipe arrangement of ratio cross valve 40 downstreams in refrigerant loop, branches into the suction side branch pipe arrangement 41,42 with the number of units equal number (being in this example two) of compressor 10,30 at branching portion 43 places.Suction side branch pipe arrangement 41 is connected with the suction side of compressor 10, and suction side branch pipe arrangement 42 is connected with the suction side of compressor 30.
In addition, in the discharge side of compressor 10, be connected with and discharge side branch pipe arrangement 44, in the discharge side of compressor 30, be connected with and discharge side branch pipe arrangement 45.On discharge side branch pipe arrangement 44,45, be respectively equipped with check-valves 44a, the 45a for stoping cold-producing medium to flow backwards to compressor 10,30 sides.Discharge side branch pipe arrangement 44 and discharge side branch pipe arrangement 45 at interflow portion 46 interflow by upstream side than cross valve 40.Between interflow portion 46 and cross valve 40, be provided with oil eliminator 47.The refrigerator oil being reclaimed by oil eliminator 47 turns back to the suction side (in this example, leaning on upstream side than cross valve 40 downstreams and than branching portion 43) of compressor 10,30 after being depressurized in capillary 48a by oil return pipe 48.
Between the pipe arrangement 44He of the discharge side branch suction side branch pipe arrangement 41 of compressor 10 by for the bypass pipe arrangement 52 of discharging side and suction side pressure equalization being connected when compressor 10 starts.On bypass pipe arrangement 52, be provided with valve 52a.Valve 52a becomes out state under the control of not shown control device before compressor 10 is about to start or while starting, the startup from compressor 10 through becoming the state of closing after the stipulated time.Similarly, between the pipe arrangement 45He of the discharge side branch suction side branch pipe arrangement 42 of compressor 30, by bypass pipe arrangement 53, connected, on bypass pipe arrangement 53, be provided with valve 53a.Valve 53a becomes out state before compressor 30 is about to start or while starting, the startup from compressor 30 through becoming the state of closing after the stipulated time.
Then, the structure of compressor 10 is illustrated simply.The compressor 10 of present embodiment is the twin-tub rotation-type compressor with two start cylinders.Compressor 10 has compression mechanical part 11, for the motor part 12 of portion of drive compression mechanism 11, for holding the closed container 13 of compression mechanical part 11 and motor part 12.The compressor 10 of present embodiment is by Exhaust Gas, to be full of the high-pressure bottle type in the space in closed container 13.
Motor part 12 has stator 14 and rotor 15.Stator 14 is fixing with respect to closed container 13.On rotor 15, embed and have bent axle 16.Bent axle 16 is by supplying with electric power to stator 14 and being driven in rotation together with rotor 15.As supply with the power supply of electric power to stator 14, in this example, adopted in order to make the variable and variable-frequency power sources that can make the driving rotating speed (frequency) of bent axle 16 change of circulating mass of refrigerant.In addition, as supply with the power supply of electric power to stator 14, also can frequency of utilization 50Hz or the general industry power supply of 60Hz.On bent axle 16, be formed with eccentric two eccentric parts (upper eccentric part 16a, lower eccentric part 16b) up and down in the 180 degree phase place ground that oppositely stagger each other.
Compression mechanical part 11 is configured in than motor part 12 position on the lower.Compression mechanical part 11 comprises: upper start cylinder 17; Lower start cylinder 18; Be used for the dividing plate 19 separating between upper start cylinder 17 and lower start cylinder 18; Be configured in the two ends up and down of the duplexer that upper start cylinder 17, lower start cylinder 18 and dividing plate 19 are laminated, be also used as base bearing 20 and the supplementary bearing 21 of sidewall; The upper rotary-piston 22 of eccentric part 16a in embedding; Embed the lower rotary-piston 23 of lower eccentric part 16b; The inner side of upper start cylinder 1 is divided into the blade (not shown) of discharge chambe and suction chamber; The inner side of lower start cylinder 18 is divided into the lower blade (not shown) of discharge chambe and suction chamber.
At the sidewall of closed container 13, in the mode of opening, be formed with connector 13a.On connector 13a, be provided with for connecting the tube connector 24 of oil equalizing pipe 55 described later.That is, on connector 13a, by tube connector 24, be connected with oil equalizing pipe 55.Connector 13a is located at the top side's of sliding part (for example, all sliding parts of compression mechanical part 11) (in this example than the top side in the upper surface of upper start cylinder 17) of ratio piston compressor structure portion 11 position.Tube connector 24 has and after closed container 13 is flatly drawn, is being bent upwards and is keeping this state to extend upward the shape forming.In this example, the top 24a of tube connector 24 is positioned at the height close with the height at the top of closed container 13.
Bottom storage at closed container 13 has refrigerator oil (lubricating oil).In Fig. 2, the fuel head OL that shows the refrigerator oil in compressor 10,30 is all in roughly than the top side in the bottom of upper start cylinder 17 and than the good state of connector 13a position on the lower.While supposing that fuel head OL is positioned at than position on the lower, the bottom of upper start cylinder 17, can the sliding part in upper start cylinder 17 produce the deficiency of refrigerator oil.
In the suction side of compressor 10, be provided with the suction reservoir 25 that the low pressure refrigerant after sucking is carried out to gas-liquid separation.Only there is the gas refrigerant sucking in reservoir 25 to be inhaled into compressor 10.
For compressor 30, there is the structure identical in fact with above-mentioned compressor 10, therefore description thereof is omitted.The running of this routine compressor 10,30, stop and turning round in frequency (rotating speed) by not shown control device, controlled independently of one another.
The top 24a and being located between the top 24a of tube connector 24 of compressor 30 that is located at the tube connector 24 of compressor 10 is connected by the oil equalizing pipe 55 on the whole with the shape of U-shaped.Thus, compressor 10,30 becomes each other by the direct-connected structure of oil equalizing pipe 55.At this, so-called " directly " refers to, is not folded with betwixt oil eliminator, fuel tank etc.By utilizing oil equalizing pipe 55 that compressor 10,30 is joined to one another, the inner space of compressor 10,30 communicates with each other.Thereby, can the one of refrigerator oil from compressor 10,30 be circulated to another one via oil equalizing pipe 55, therefore, can eliminate at once the inhomogeneous of refrigerator oil.In addition, can by oil equalizing pipe 55, make the internal pressure pressure equalization of compressor 10,30, therefore, also can prevent the inhomogeneous of refrigerator oil that the difference by the small operating condition of compressor 10,30 causes.
On oil equalizing pipe 55, be provided with valve (open and close valve) 55a.Valve 55a opens and closes oil equalizing pipe 55 under the control of not shown control device.In the present embodiment, when compressor 10,30 all stops, or compressor 10,30 is when turn round with same frequency (being only called below " same frequency ") in fact each other, valve 55a becomes out state, allows the circulations such as refrigerator oil in oil equalizing pipe 55 and cold-producing medium.In addition, only have one when running in compressor 10,30, or compressor 10,30 is when turn round with different frequency, valve 55a becomes the state of closing, and the circulation of the refrigerator oil in oil equalizing pipe 55 and cold-producing medium etc. is prevented from.Thus, valve 55a has while only having one running in compressor 10,30, or at compressor 10,30 during with mutually different frequency run, prevent that together with check-valves 44a, 45a one in compressor 10,30 cold-producing medium after compressed from flowing into the function of another one.Thereby in other words, by being provided with valve 55a and check-valves 44a, 45a, can make only has one running and compressor 10,30 with mutual different frequency run in compressor 10,30.
Then, the distinctive action of the freezing cycle device 2 of present embodiment is described.First, to compressor 10,30, the two action during each other with same frequency run describes.At compressor 10,30, during each other with same frequency run, as mentioned above, the valve 55a that is located at oil equalizing pipe 55 becomes out state.Thus, the inner space of the inner space of compressor 10 and compressor 30 is communicated with via oil equalizing pipe 55.Therefore, it is too much that the one in compressor 10,30 becomes oil mass, and another one becomes in the very few situation of oil mass, the unnecessary refrigerator oil of a compressor can be supplied with to another compressor via oil equalizing pipe 55.At this, in the refrigerator oil of supplying with via oil equalizing pipe 55, not only contain the refrigerator oil of liquid condition, also contain vaporific refrigerator oil.Thereby, the unnecessary refrigerator oil of a compressor can be supplied with to another compressor, the pasta that is not only limited to a refrigerator oil in compressor has reached the situation of the position of connector 13a.Thus, can eliminate at once the inhomogeneous of refrigerator oil in compressor 10,30.In addition, the inner space of the inner space of compressor 10 and compressor 30 is communicated with via oil equalizing pipe 55, thereby makes two inner space pressure equalizations.Therefore, can prevent the inhomogeneous of refrigerator oil that the difference because of the small operating condition between compressor 10,30 causes.
Action when then, compressor 10,30 is all stopped describes.When compressor 10,30 all stops, as mentioned above, the valve 55a that is located at oil equalizing pipe 55 becomes out state.Thus, the inner space of the inner space of compressor 10 and compressor 30 is communicated with via oil equalizing pipe 55.Therefore, it is too much that the one in compressor 10,30 becomes oil mass, and another one becomes in the very few situation of oil mass, the unnecessary refrigerator oil of a compressor can be supplied with to another compressor via oil equalizing pipe 55.
Then, in compressor 10,30, only there is one when running (during one-sided running.Below sometimes also by 3 above compressors only the state of some running be called one-sided running) action describe.At this, only compressor 10 runnings, compressor 30 stops.When one-sided running, the pressure in the inner space of compressor 10,30 produces difference, and therefore, as mentioned above, the valve 55a that is located at oil equalizing pipe 55 becomes the state of closing.Refrigerator oil is discharged together with compressed refrigerant from operating compressor 10, and a part for refrigerator oil turns back in compressor 10 via oil eliminator 47, oil return pipe 48 and suction reservoir 25.With respect to this, refrigerator oil can not discharged from the compressor 30 stopping, and only has a part for the refrigerator oil of compressor 10 discharges from running to return via oil eliminator 47, oil return pipe 48 and suction reservoir 25.In addition, at the discharge side branch pipe arrangement 45 of compressor 30 sides, be provided with check-valves 45a, therefore, prevent that cold-producing medium and the refrigerator oil compressor 10 from running from flowing backwards to the compressor 30 in stopping.
Thus, when one-sided running, the on-stream compressor 10 of refrigerator oil reduces gradually, in the compressor 30 of refrigerator oil in stopping, increasing gradually.But when one-sided running finishes while stopping (compressor 10,30 the two), as mentioned above, the valve 55a that is located at oil equalizing pipe 55 becomes out state.Therefore, when one-sided running finishes, at compressor 30, become oil mass too much and compressor 10 becomes oil mass very few in the situation that, in the stopped process of compressor 10,30, the unnecessary refrigerator oil of compressor 30 can be supplied with to compressor 10 via oil equalizing pipe 55.Thereby, before once starting, can guarantee required fuel head in the two at compressor 10,30 on compressor 10 or compressor 30.Thus, the unfavorable condition that the refrigerator oil deficiency in the time of can preventing by the starting of compressor 10,30 next time causes, therefore, the reliability in the time of can improving next time the starting of compressor 10,30, and, can improve the durability of compressor 10,30.Like this, when one-sided running finishes, in the situation that the one in compressor 10,30 becomes oil mass too much, to become oil mass very few for another one, can obtain the significant especially effect of present embodiment.
Then, to compressor 10,30, the action during with mutually different frequency run describes.At this, compressor 10 is with relatively high frequency run, and compressor 30 is with relatively low frequency run.At compressor 10,30 during with mutually different frequency run, the pressure in the inner space of compressor 10,30 produces difference, and therefore, as mentioned above, the valve 55a that is located at oil equalizing pipe 55 becomes the state of closing.Now, produce that refrigerator oil with the operating compressor 10 of high-frequency reduces gradually and increase gradually such phenomenon with the refrigerator oil of the operating compressor 30 of low frequency.But when the running of compressor 10,30 finishes, as mentioned above, the valve 55a that is located at oil equalizing pipe 55 becomes out state.Therefore, when the running of compressor 10,30 finishes, at compressor 30, become oil mass too much and compressor 10 becomes oil mass very few in the situation that, in the stopped process of compressor 10,30, the unnecessary refrigerator oil of compressor 30 can be supplied with to compressor 10 via oil equalizing pipe 55.Thereby, before once starting, can guarantee required fuel head in the two at compressor 10,30 on compressor 10 or compressor 30.Thus, the unfavorable condition that the refrigerator oil deficiency in the time of can preventing by the starting of compressor 10,30 next time causes, therefore, the reliability in the time of can improving next time the starting of compressor 10,30, and can improve the durability of compressor 10,30.
In addition, the reliability while carrying out one-sided running by improving as described above, can select the running of total running or minimizing operating number, to can be that compressor is used in maximum place at compressor efficiency for the operating point based on air conditions.That is,, even if refrigerating capacity is on the whole identical, also can by the frequency of change multiple compressors, make operating number different.For example, in the situation that compressor is two, according to air conditions, only make 1 compressor turn round with 60rps, or make two compressors respectively with 30rps running, can select the good side of compressor efficiency.Thereby, compared with the past, can obtain freezing cycle device and air conditioner that energy-saving effect is higher.
Fig. 3 means the refrigerant loop figure as the major part structure of the freezing cycle device without oil equalizing pipe 55 and valve 55a of the comparative example of the freezing cycle device 2 of present embodiment.As shown in Figure 3, in this freezing cycle device, discharge in side branch pipe arrangement 44 than check-valves 44a by the part of upstream side be located between the top 24a of tube connector 24 of compressor 10 and connected by oil return pipe 56.In addition, discharge being connected by oil return pipe 57 with being located between the top 24a of tube connector 24 of compressor 30 by the part of upstream side than check-valves 45a in side branch pipe arrangement 45.In this structure, a part for the refrigerator oil of discharging together with cold-producing medium to discharge side branch pipe arrangement 44,45 from compressor 10,30, turns back to compressor 10,30 via oil return pipe 56,57.
In the structure shown in Fig. 3, when the one-sided running that for example only compressor 30 turns round, in on-stream compressor 30, refrigerator oil reduces gradually, and in the compressor 10 in stopping, refrigerator oil increases gradually.Now, at compressor 30, become oil mass too much and compressor 10 becomes oil mass very few in the situation that, different from present embodiment, after one-sided running finishes, (compressor 10,30 stopped after) also can maintain this state.At this, in Fig. 3, the height of the fuel head OL that shows compressor 30 in lower start cylinder 18 and can produce the not enough state of refrigerator oil in upper start cylinder 17.Therefore, become the unfavorable condition that oil mass very few compressor 30 causes in the upper deficiency likely producing while once starting by refrigerator oil.
Then, the whole cooling operation action of the freezing cycle device 2 of present embodiment and air conditioner 1 is described simply.The gas refrigerant of the HTHP of being discharged by compressor 10,30 compressions, flows into outdoor heat exchanger 50 via cross valve 40.Flowed into the gas refrigerant of outdoor heat exchanger 50, the condensation because the extraneous gas with being blowed with fan 51 by off-premises station carries out heat exchange, becomes the cold-producing medium of low temperature, from outdoor heat exchanger 50, flows out.Utilize expansion gear 60 to make the cold-producing medium flowing out from outdoor heat exchanger 50 expand and reduce pressure, become the gas-liquid two-phase cold-producing medium of low-temp low-pressure.This gas-liquid two-phase cold-producing medium flows into the indoor heat exchanger 70 of indoor set 200, because the room air with being blowed by used for indoor machine fan 71 carries out heat exchange, evaporates, and becomes the gas refrigerant of low-temp low-pressure and flows out from indoor heat exchanger 70.Now, cooled dose heat absorption and cooled room air becomes air conditioning air (cold wind), from the blow-off outlet of indoor set 200, be blown out to indoor (air conditioning object space).From indoor heat exchanger 70 effluent air cold-producing mediums, via cross valve 40, be inhaled into compressor 10,30, again compressed.Repeat above action.In above action, not only refrigerant gas circulates in refrigerant loop, and vaporific refrigerator oil also circulates in refrigerant loop.
Then, the running action that heats of freezing cycle device 2 and air conditioner 1 is described.The gas refrigerant of the HTHP of being discharged by compressor 10,30 compressions, the indoor heat exchanger 7 of inflow indoor set 200 via cross valve 40.Flowed into the gas refrigerant of indoor heat exchanger 70, the condensation because the room air with being blowed by used for indoor machine fan 71 carries out heat exchange, becomes the cold-producing medium of low temperature, from indoor heat exchanger 70, flows out.Now, the room air from cold-producing medium heat absorption and being heated becomes air conditioning air (warm braw), from the blow-off outlet of indoor set 200, is blown out to indoor.Utilize expansion gear 60 to make the cold-producing medium flowing out from indoor heat exchanger 70 expand and reduce pressure, become the gas-liquid two-phase cold-producing medium of low-temp low-pressure.This gas-liquid two-phase cold-producing medium flows into outdoor heat exchanger 50, because the air with being blowed with fan 51 by off-premises station carries out heat exchange, evaporates, and becomes the gas refrigerant of low-temp low-pressure, and flows out from outdoor heat exchanger 50.From outdoor heat exchanger 50 effluent air cold-producing mediums, via cross valve 40, be inhaled into compressor 10,30, again compressed.Repeat above action.In above action, not only refrigerant gas circulates in refrigerant loop, and vaporific refrigerator oil also circulates in refrigerant loop.
As described above, in the present embodiment, be provided with and compressor 10,30 be connected to each other and the inner space of compressor 10,30 is communicated with, make the one of refrigerator oil from compressor 10,30 to the oil equalizing pipe 55 of another one circulation.Adopt this structure, unnecessary refrigerator oil (liquid condition or vaporific) can be supplied with to (equal oily effect) via oil equalizing pipe 55 to the another one becoming in the very few compressor of oil mass 10,30 from the one becoming the too much compressor of oil mass 10,30.Thereby, can eliminate at once the inhomogeneous of maintenance oil mass in compressor 10,30.In addition, adopt this structure, can make compressor 10,30 inner space pressure equalization (all pressing effect) separately by oil equalizing pipe 55.Thereby, can prevent the inhomogeneous of refrigerator oil that the difference by 10,30 small operating conditions of compressor causes.
In addition, in the present embodiment, be provided with the valve 55a for oil equalizing pipe 55 is opened and closed.Adopt this structure, can avoid the fuel head of another compressor when the fuel head of a compressor has reduced to be also reduced to the situation of bottom.Thereby, can in each compressor 10,30, guarantee required fuel head.
In addition, in the present embodiment, at the sidewall of the closed container 13 of compressor 10,30, be formed with the connector 13a being connected with oil equalizing pipe 55, connector 13a is located at the compression mechanical part 11 top sides' of ratio piston compressor 10,30 position.Adopt this structure, can avoid when the fuel head of a compressor has reduced, the fuel head of another compressor is also reduced to the situation of bottom.Thereby, can avoid all no longer guaranteeing the situation of required fuel head at compressor 10,30 in the two.
In addition, in the present embodiment, valve 55a when compressor 10,30 all stops or compressor 10,30 become out state during each other with same frequency run, at compressor 10,30, when only some (in this example, being the one in compressor 10,30) when running or compressor 10,30 are with mutually different frequency run, become the state of closing.Adopt this structure, when the running of compressor 10,30 finishes, at compressor 30, become oil mass too much and compressor 10 becomes oil mass very few in the situation that, can in the stopped process of compressor 10,30, the unnecessary refrigerator oil of compressor 30 be supplied with to compressor 10 via oil equalizing pipe 55.Thereby, before once starting, can guarantee required fuel head in the two at compressor 10,30 on compressor 10 or compressor 30, therefore, the reliability in the time of can improving next time the starting of compressor 10,30.
Other embodiments.
The utility model is not limited to above-mentioned embodiment, can carry out various distortion.
For example, in the above-described embodiment, the freezing cycle device that two compressors are together in parallel of take is enumerated as example, but the utility model also can be applicable to the freezing cycle device that 3 above compressor parallels are got up.Fig. 4～Fig. 6 means the top view as the summary of the example of the connection structure of the oil equalizing pipe in the freezing cycle device with 3 above compressors of the variation of above-mentioned embodiment.
In the example shown in Fig. 4, in refrigerant loop, be provided with 3 compressors 301～303 in parallel.Compressor 301～303 has respectively top and is branched off into 2 gangs of tube connector 301a～303a that form.Between top of tube connector 301a and a top of tube connector 302a, by oil equalizing pipe 311, connect.Between a top of another top of tube connector 302a and tube connector 303a, by oil equalizing pipe 312, connect.Between another top of tube connector 303a and another top of tube connector 301a, by oil equalizing pipe 313, connect.On oil equalizing pipe 311～313, be respectively equipped with valve 311a～313a.That is,, in the example shown in Fig. 4, by the oil equalizing pipe 311～313 that is provided with valve 311a～313a, the mode with 1 pair 1 is connected with two other compressors 3 compressors 301～303 respectively.
Example to the open and-shut mode of the valve 311a～313a in the example shown in Fig. 4 describes.At compressor 301～303 during all with same frequency run or when compressor 301～303 all stops, all valve 311a～313a become out state.At compressor 301,302 when with same frequency run, compressor 303 stops when only compressor 303 is with different frequency run (or), only there is the valve 311a of 301,302, compressor to become out state, valve 312a, 313a in addition become the state of closing.When only there being compressor 301 runnings, compressor 302,303 stops, all valve 311a～313a become the state of closing.At compressor 301,302 when with mutually different frequency run, compressor 303 stops, or compressor 301～303 is during all with different frequency run, and all valve 311a～313a become the state of closing.Adopt the structure shown in Fig. 4, make as described above valve 311a～313a action, can obtain the effect same with above-mentioned embodiment.
In the example shown in Fig. 5, in refrigerant loop, be provided with 4 compressors 301～304 in parallel.The radial portion 321～324 that the oil equalizing pipe 320 that adopted in this embodiment has central part 325 and is the quantity that radial number of units that branch out and compressor 301～304 equates from central part 325.Radial portion 321～324 top is separately connected in compressor 301～304(tube connector).In radial portion 321～324, be respectively equipped with valve 321a～324a.That is,, in the example shown in Fig. 5, compressor 301～304 is connected with central part 325 via the radial portion 321～324 that is provided with valve 321a～324a respectively.
Example to the open and-shut mode of the valve 321a～324a in the example shown in Fig. 5 describes.At 4 compressors 301～304 during all with same frequency run, or 4 compressors 301～304 are when all stop, and all valve 321a～324a become out state.At 3 compressors 301,302,303, with same frequency run, when 1 compressor 304 stops while only having 1 compressor 304 with different frequency run (or), valve 321a～323a becomes out state, and only valve 324a becomes the state of closing.When only having 1 compressor 301 runnings, 3 compressors 302,303,304 to stop, all valve 321a～324a become the state of closing.When two compressors 301,302 stop with different frequency runs, 1 compressor 304 with same frequency run, 1 compressor 303, valve 321a, 322a become out state, and valve 323a, 324a become the state of closing.At two compressors 301,302 with same frequency run, two compressors 303,304 during with the different same frequency run of the frequency from compressor 301,302, valve 321a, 322a become out state, valve 323a, 324a become the state of closing, or valve 321a, 322a become the state of closing, valve 323a, 324a become out state.
Adopt the structure shown in Fig. 5, by making as described above valve 321a～324a move, can obtain the effect same with above-mentioned embodiment.In addition, with structure shown in Fig. 4 relatively time, in the structure shown in Fig. 5, can cut down the quantity of the valve 321a～324a of the number of units of compressor 301～304 when more when above (4).
In the example shown in Fig. 6, in refrigerant loop, be provided with 4 compressors 301～304 in parallel.The oil equalizing pipe 330 adopting in this example, has the radial portion 331～334 that is located in the form of a ring the annulus 335 at center and is respectively the quantity that radial number of units that branch out and compressor 301～304 equates from annulus 335.Radial portion 331～334 top is separately connected in compressor 301～304(tube connector).In radial portion 331～334, be respectively equipped with valve 331a～334a.That is,, in the example shown in Fig. 6, compressor 301～304 is connected with annulus 335 via the radial portion 331～334 that is provided with valve 331a～334a respectively.
Adopt the structure shown in Fig. 6, by the valve 321a～324a with shown in Fig. 5, similarly make valve 331a～334a move, can obtain the effect same with above-mentioned embodiment.In addition, in the structure shown in Fig. 6, with structure shown in Fig. 5 relatively time, can simplify the branch construct of the number of units of compressor 301～304 oil equalizing pipe 330 when more.
In addition, in the above-described embodiment, the moving cylinder rotary compressor of the double cropping of take is enumerated as example, but the utility model also can be applicable to have the rotary compressor of 1 start cylinder or 3 above start cylinders.In addition, the utility model also can be applicable to rotary compressor compressor in addition.
In addition, each above-mentioned embodiment, variation can combination with one another be implemented.
Description of reference numerals
1, air conditioner; 2, freezing cycle device; 10,30,301,302,303,304, compressor; 11, compression mechanical part; 12, motor part; 13, closed container; 13a, connector; 14, stator; 15, rotor; 16, bent axle; 16a, upper eccentric part; 16b, lower eccentric part; 17, upper start cylinder; 18, lower start cylinder; 19, dividing plate; 20, base bearing; 21, supplementary bearing; 22, upper rotary-piston; 23, lower rotary-piston; 24,301a, 302a, 303a, tube connector; 24a, top; 25, suck reservoir; 40, cross valve; 41,42, suction side branch pipe arrangement; 43, branching portion; 44,45, discharge side branch pipe arrangement; 44a, 45a, check-valves; 46, interflow portion; 47, oil eliminator; 48, oil return pipe; 48a, capillary; 50, outdoor heat exchanger; 51, off-premises station fan; 52,53, bypass pipe arrangement; 52a, 53a, valve; 55,311,312,313,320,330, oil equalizing pipe; 55a, 311a, 312a, 313a, 321a, 322a, 323a, 324a, 331a, 332a, 333a, 334a, valve; 56,57, oil return pipe; 60, expansion gear; 70, indoor heat exchanger; 71, used for indoor machine fan; 100, off-premises station; 200, indoor set; 321,322,323,324,331,332,333,334, radial portion; 325, central part; 335, annulus; OL, fuel head.
Claims (4)
1. a freezing cycle device, it is the freezing cycle device with a plurality of compressors in parallel, it is characterized in that, this freezing cycle device comprises:
Oil equalizing pipe, it is joined to one another above-mentioned compressor and the inner space of above-mentioned compressor is communicated with, and refrigerator oil is circulated between above-mentioned compressor;
Valve, it opens and closes above-mentioned oil equalizing pipe.
2. freezing cycle device according to claim 1, is characterized in that,
On the sidewall of above-mentioned compressor, be formed with the connector being connected with above-mentioned oil equalizing pipe,
Above-mentioned connector is located at than the top side's of compression mechanical part of above-mentioned compressor position.
3. freezing cycle device according to claim 1, is characterized in that,
When above-mentioned compressor all stops or above-mentioned compressor during each other with same frequency run, above-mentioned valve becomes out state,
Some when running only in above-mentioned compressor, or above-mentioned compressor is during with mutually different frequency run, and above-mentioned valve becomes the state of closing.
4. an air conditioner, is characterized in that,
It comprises the freezing cycle device described in any one in claim 1～3.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013072909A JP2014196874A (en) | 2013-03-29 | 2013-03-29 | Refrigeration cycle device and air conditioner including the same |
| JP2013-072909 | 2013-03-29 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203785327U true CN203785327U (en) | 2014-08-20 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410120860.9A Pending CN104075494A (en) | 2013-03-29 | 2014-03-28 | Refrigeration circulation device and air conditioner with the refrigeration circulation device |
| CN201420145201.6U Expired - Fee Related CN203785327U (en) | 2013-03-29 | 2014-03-28 | Refrigeration circulation device and air conditioner with same |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410120860.9A Pending CN104075494A (en) | 2013-03-29 | 2014-03-28 | Refrigeration circulation device and air conditioner with the refrigeration circulation device |
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| Country | Link |
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| JP (1) | JP2014196874A (en) |
| CN (2) | CN104075494A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104075494A (en) * | 2013-03-29 | 2014-10-01 | 三菱电机株式会社 | Refrigeration circulation device and air conditioner with the refrigeration circulation device |
| TWI656310B (en) * | 2016-02-26 | 2019-04-11 | Ｌｇ電子股份有限公司 | High pressure compressor and refrigerating machine having the same |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104633998B (en) * | 2015-02-12 | 2017-10-31 | 三菱电机(广州)压缩机有限公司 | Rotor-type compressor parallel system |
| CN105135768A (en) * | 2015-09-30 | 2015-12-09 | 海信容声(广东)冷柜有限公司 | Refrigeration equipment and control method thereof |
| JP6970363B1 (en) * | 2020-09-30 | 2021-11-24 | ダイキン工業株式会社 | Compressor |
| WO2023195042A1 (en) * | 2022-04-04 | 2023-10-12 | 三菱電機株式会社 | Refrigeration cycle device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0282057A (en) * | 1988-09-19 | 1990-03-22 | Matsushita Refrig Co Ltd | Heat pump type air conditioner |
| JPH02264168A (en) * | 1989-04-05 | 1990-10-26 | Hitachi Ltd | Freezing device |
| JP3163121B2 (en) * | 1991-06-28 | 2001-05-08 | 東芝キヤリア株式会社 | Air conditioner |
| JP2955424B2 (en) * | 1992-03-10 | 1999-10-04 | 東芝エー・ブイ・イー株式会社 | Air conditioner |
| JP2000046418A (en) * | 1998-07-30 | 2000-02-18 | Matsushita Electric Ind Co Ltd | Inverter type air conditioner |
| JP2004205175A (en) * | 2002-12-26 | 2004-07-22 | Toshiba Kyaria Kk | Refrigerator |
| JP4325751B2 (en) * | 2003-03-25 | 2009-09-02 | 東芝キヤリア株式会社 | Refrigeration cycle equipment |
| CN100487346C (en) * | 2004-07-08 | 2009-05-13 | 乐金电子(天津)电器有限公司 | Air conditioner |
| US8408024B2 (en) * | 2008-05-23 | 2013-04-02 | Panasonic Corporation | Fluid machine and refrigeration cycle apparatus |
| CN101303180A (en) * | 2008-06-13 | 2008-11-12 | 广东志高空调有限公司 | Multiple-compressor parallel wind cooling module air conditioner system |
| JP2011141078A (en) * | 2010-01-07 | 2011-07-21 | Panasonic Corp | Refrigeration cycle apparatus |
| JP2014196874A (en) * | 2013-03-29 | 2014-10-16 | 三菱電機株式会社 | Refrigeration cycle device and air conditioner including the same |
-
2013
- 2013-03-29 JP JP2013072909A patent/JP2014196874A/en active Pending
-
2014
- 2014-03-28 CN CN201410120860.9A patent/CN104075494A/en active Pending
- 2014-03-28 CN CN201420145201.6U patent/CN203785327U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104075494A (en) * | 2013-03-29 | 2014-10-01 | 三菱电机株式会社 | Refrigeration circulation device and air conditioner with the refrigeration circulation device |
| TWI656310B (en) * | 2016-02-26 | 2019-04-11 | Ｌｇ電子股份有限公司 | High pressure compressor and refrigerating machine having the same |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2014196874A (en) | 2014-10-16 |
| CN104075494A (en) | 2014-10-01 |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140820 |