CN201772684U - Two-stage rotor type compressor and decompression and defrosting heat pump circulation system - Google Patents
Two-stage rotor type compressor and decompression and defrosting heat pump circulation system Download PDFInfo
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- CN201772684U CN201772684U CN2010202045292U CN201020204529U CN201772684U CN 201772684 U CN201772684 U CN 201772684U CN 2010202045292 U CN2010202045292 U CN 2010202045292U CN 201020204529 U CN201020204529 U CN 201020204529U CN 201772684 U CN201772684 U CN 201772684U
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Abstract
The utility model relates to a two-stage rotor type compressor and decompression and defrosting heat pump circulation system, which comprises a compressor, an air cooler, a filter, an electronic expansion valve, an evaporator and a gas-liquid separator. The compressor comprises a primary compression unit, a secondary compression unit, a primary air suction port, a primary exhaust port, a secondary air suction port and a secondary exhaust port, the secondary exhaust port is connected with the air cooler, the air cooler is connected with the primary air suction port after being successively connected with the filter, the electronic expansion valve, the evaporator and the gas-liquid separator, pressure between the gas-liquid separator and the primary compression unit is low, pressure between the primary compression unit and the secondary compression unit is medium, pressure at rear of the secondary compression unit is high, the compressor further comprises a communicating valve, and the communicating valve is disposed inside or outside the compressor so as to communicate low pressure with high pressure. Compared with the prior art, the two-stage rotor type compressor and decompression and defrosting heat pump circulation system has the advantages of stable operation, capabilities of increasing reliability of the compressor and reducing noise and the like.
Description
Technical field
The utility model relates to compressor, especially relates to the heat pump circulating system of a kind of two-stage rotor-type compressor and band pressure release and defrosting.
Background technology
Present high back pressure two-stage rolling rotor-type compressor schematic diagram such as Fig. 1, it comprises two compression units (one-level compressor unit 1 and secondary compression unit 2), and each compression unit is respectively the discharge capacity of the discharge capacity of rotor-type compressor structure and secondary compression unit 2 less than one-level compression unit 1.Motor 3 drives the operation of two compression units by bent axle.The low pressure Ps gas that comes from evaporator outlet enters the one-level compression unit by one-level air entry 4, after the one-level compression, form intermediate pressure Pm, the back is discharged to outside the housing by one-level steam vent 5, the medium pressure gas that one-level exhaust outlet 5 is discharged can directly enter secondary suction hole 6, or after cooling off by intercooler, enter secondary air entry 6, again through after 5 compressions of secondary compression unit, form high pressure P d gas and be discharged to enclosure interior, after enter secondary exhaust outlet 7 and discharge, enter condenser (or air cooler).
Adopt hot-gas bypass defrosting and reverse cycle defrosting schematic diagram at present shown in Fig. 2～4, solid line is the normal heat pump operation among the figure, and dotted line is a Defrost operation; Fig. 2 is the heat pump circulating system of band high pressure bypass defrost: this system comprises compressor, air cooler 8, filter 9, electric expansion valve 10, magnetic valve 11, evaporimeter 12, gas-liquid separator 13, after described air cooler 8 connects filter 9 and electric expansion valve 10 successively, in parallel with magnetic valve 11, back in parallel one end connects the secondary exhaust outlet 7 of compressor, the other end connects evaporimeter 12, evaporimeter 12 connects the one-level air entry 4 of compressor by gas-liquid separator 13, normal heat pump circulation time magnetic valve 11 cuts out, the gases at high pressure that secondary exhaust outlet 7 is discharged are successively through air cooler 8 coolings, filter 9 filters, electric expansion valve 10 expands, evaporimeter 12 evaporations, the one-level air entry 4 of compressor is returned in gas-liquid separator 13 gas-liquid separations; During defrost cycle, magnetic valve 11 is opened, electric expansion valve 10 standard-sized sheets, and the gas that secondary exhaust outlet 7 is discharged directly enters evaporimeter 12 evaporations by magnetic valve 11, enters one-level air entry 4 then after gas-liquid separator 13 separates, and adopts the secondary exhaust to defrost.Be illustrated in figure 3 as the heat pump circulating system of pressing bypass defrost in the band: magnetic valve 11 connects secondary air entry 6, and normal heat pump circulation time magnetic valve 11 cuts out; During defrost cycle, magnetic valve 11 is opened, and adopts the one-level exhaust to defrost; Fig. 4 is for adopting the heat pump circulating system of reverse cycle defrosting: flow to by four-way change-over valve 11 ' control heat pump agent.Four-way change-over valve 11 ' connects secondary exhaust outlet 7, and the secondary exhaust flows to condenser (air cooler) through four-way change-over valve during the normal heat pump operation; During Defrost operation, the four-way change-over valve commutation, the secondary exhaust flows to evaporimeter through four-way change-over valve.
Above high back pressure two-stage rotor-type compressor may run into the problem aspect three in startup, underrun and defrost process:
The startup stage:
Before startup, system pressure is in poised state, and the one-level pressure of inspiration(Pi) is higher relatively; Start the back and participate in Fig. 5, the one-level exhaust forms higher pressure P m rapidly, this moment is because the discharge capacity of secondary compression unit is less and secondary exhaust side capacity is bigger, the high side pressure Pd rate of climb is relatively slow, therefore the secondary pressure of inspiration(Pi) may occur (is Pm＞Pd) greater than the phenomenon of secondary pressure at expulsion, thereby cause the secondary air bleeding valve to be in open mode all the time, be unfavorable for the assurance of the reliability of secondary air bleeding valve like this, throttling phenomenon may occur when cold-producing medium is through the secondary air bleeding valve this moment; Because the back pressure of two grade blades is the pressure P d in the housing, during Pd＜Pm, the pressure of its back pressure can occur, thereby cause the blade fluctuation of service less than secondary suction muffler (Pm) or secondary discharge chamber, blade and piston may occur and break away from, bump, " prancing " phenomenon;
2. underrun (low-pressure ratio operation)
Two-stage rolling rotor-type compressor is in service, as shown in Figure 6, pressure of inspiration(Pi) Ps remains unchanged, along with the reduction of overall pressure tatio, overall pressure tatio is finished by the one-level compression gradually, when overall pressure tatio is reduced to certain numerical value, there is a critical pressure ratio (Pc), this moment, the compression of overall pressure tatio was finished by one-level fully, and promptly this moment, intermediate pressure Pm and high side pressure Pd equated that secondary has not produced compression; When overall pressure tatio continued to reduce, the phenomenon of intermediate pressure Pm greater than high side pressure Pd may appear.When Pm＞Pd phenomenon occurring, equally the problems referred to above can appear.The size of critical pressure ratio is relevant with the compressor arrangements such as volumetric ratio of one/secondary;
3. Defrost operation process
No matter be to adopt hot-gas bypass defrosting or reverse cycle defrosting, when when defrost cycle is changed, pressure of inspiration(Pi) all can occur and increase, the phenomenon that pressure at expulsion descends; As shown in Figure 7, for the agent of freon heat pump is inhaled in defrost process/change procedure of pressure at expulsion, wherein among Fig. 7 a-●-be exhaust,-■-be air-breathing, among Fig. 7 b---be the pressure at expulsion of hot-gas bypass defrosting, pressure of inspiration(Pi) for the hot-gas bypass defrosting,--be the pressure of inspiration(Pi) of reverse cycle defrosting,---the be pressure at expulsion of reverse cycle defrosting, when adopting above-mentioned two-stage rotor-type compressor, in the defrost process, the phenomenon of overall pressure tatio less than critical pressure ratio (Pc) may appear promptly, this moment, therefore Pm＞Pd above-mentioned same problem can occur.If CO
2System and since when operation pressure reduction more greatly, when defrost cycle was changed, the conversion of suction and discharge pressure may be more violent, pressure ratio may be littler.
Summary of the invention
The purpose of this utility model is exactly that a kind of stable, reliability of improving compressor is provided in order to overcome the defective that above-mentioned prior art exists, and reduces the two-stage rotor-type compressor of noise and the heat pump circulating system of band pressure release and defrosting.
The purpose of this utility model can be achieved through the following technical solutions: the heat pump circulating system of two-stage rotor-type compressor and band pressure release and defrosting, this system comprises compressor, air cooler, filter, electric expansion valve, evaporimeter, gas-liquid separator, described compressor comprises the one-level compression unit, the secondary compression unit, the one-level air entry, the one-level exhaust outlet, the secondary air entry, the secondary exhaust outlet, described secondary exhaust outlet connects air cooler, air cooler connects filter successively, electric expansion valve, evaporimeter, behind the gas-liquid separator, the one-level air entry that connects compressor, constitute low pressure between described gas-liquid separator and the one-level compression unit, press in constituting between one-level compression unit and the secondary compression unit, it behind the secondary compression unit high pressure, it is characterized in that, also comprise communicating valve, it is inner or outside that this communicating valve is arranged on the compressor that low pressure is communicated with high pressure.
Described communicating valve is check valve or magnetic valve.
Described communicating valve one end connects the secondary exhaust outlet, and the other end connects the one-level exhaust outlet.
Be provided with magnetic valve between described secondary exhaust outlet and the evaporimeter.
Be provided with magnetic valve between described secondary air entry and the evaporimeter.
Be provided with four-way change-over valve between described secondary exhaust outlet, evaporimeter, air cooler and the gas-liquid separator.
Compared with prior art, the utility model can be avoided the pressure phenomenon of blade backpressure less than secondary suction muffler or secondary discharge chamber, thereby better guarantees blade stable operation, improves the reliability of compressor, reduces noise.
Description of drawings
Fig. 1 is existing high back pressure two-stage rolling rotor-type compressor schematic diagram;
Fig. 2 is the schematic diagram of the heat pump circulating system of existing band high pressure bypass defrost;
Fig. 3 is for pressing the schematic diagram of the heat pump circulating system of bypass defrost in the existing band;
Fig. 4 is the schematic diagram of the heat pump circulating system of existing band reverse cycle defrosting;
Fig. 5 changes schematic diagram for pressure after having compressor start now;
Fig. 6 for existing compressor start after pressure with the variation schematic diagram of overall pressure tatio;
Fig. 7 a is existing first kind of defrost process suction and discharge pressure trend figure;
Fig. 7 b is existing second kind of defrost process suction and discharge pressure trend figure;
Fig. 8 is the heat pump circulating system schematic diagram of pressure release of the utility model band and high pressure bypass defrost;
Fig. 9 is the heat pump circulating system schematic diagram of pressure release of the utility model band and middle pressure bypass defrost;
Figure 10 is the heat pump circulating system schematic diagram of pressure release of the utility model band and reverse cycle defrosting.
The specific embodiment
Below in conjunction with the drawings and specific embodiments the utility model is elaborated.
As shown in Figure 8, the heat pump circulating system of two-stage rotor-type compressor and band pressure release and defrosting, this system comprises compressor, air cooler 8, filter 9, electric expansion valve 10, magnetic valve 11, evaporimeter 12, gas-liquid separator 13, described compressor comprises one-level compression unit 1, secondary compression unit 2, motor 3, one-level air entry 4, one-level exhaust outlet 5, secondary air entry 6, secondary exhaust outlet 7, each compression unit is respectively the discharge capacity of the discharge capacity of rotor-type compressor structure and secondary compression unit 2 less than one-level compression unit 1, and motor 3 drives one- level compression unit 1 and 2 operations of secondary compression unit by bent axle.After described air cooler 8 connects filter 9 and electric expansion valve 10 successively, in parallel with magnetic valve 11, back in parallel one end connects the secondary exhaust outlet 7 of compressor, the other end connects evaporimeter 12, evaporimeter 12 connects the one-level air entry 4 of compressor by gas-liquid separator 13, constitute low pressure Ps between described gas-liquid separator 13 and the one-level compression unit, press Pm in constituting between one-level compression unit and the secondary compression unit, behind the secondary compression unit high pressure P d, the low pressure Ps gas that comes from evaporator outlet enters the one-level compression unit by one-level air entry 4, after the one-level compression, form intermediate pressure Pm, the back is discharged to outside the housing by one-level steam vent 5, and the medium pressure gas that one-level exhaust outlet 5 is discharged can directly enter secondary suction hole 6, or after cooling off by intercooler, enter secondary air entry 6, through after 2 compressions of secondary compression unit, form high pressure P d gas and also be discharged to enclosure interior again, after enter secondary exhaust outlet 7 and discharge.
Normal heat pump circulation time magnetic valve 11 cuts out, the gases at high pressure that secondary exhaust outlet 7 is discharged filter through air cooler 8 coolings, filter 9 successively, electric expansion valve 10 expands, evaporimeter 12 evaporates, gas-liquid separator 13 gas-liquid separations, returns the one-level air entry 4 of compressor; During defrost cycle, magnetic valve 11 is opened, electric expansion valve 10 standard-sized sheets, and the gas that secondary exhaust outlet 7 is discharged directly enters evaporimeter 12 evaporations by magnetic valve 11, enters one-level air entry 4 then after gas-liquid separator 13 separates, and adopts the secondary exhaust to defrost.
Between secondary exhaust outlet 7 and one-level exhaust outlet 5, be provided with check valve 14, the trend of this check valve 14 is that one-level exhaust outlet 5 is to secondary exhaust outlet 7, as the intermediate pressure Pm of compressor during greater than high side pressure Pd, check valve 14 is opened automatically, this moment intermediate pressure Pm and high side pressure Pd bypass, make the secondary compression unit be in idling conditions, thereby further improve two grade blade operation stabilities.
As shown in Figure 9, the heat pump circulating system of two-stage rotor-type compressor and band pressure release and defrosting, this system comprises compressor, air cooler 8, filter 9, electric expansion valve 10, magnetic valve 11, evaporimeter 12, gas-liquid separator 13, described compressor comprises one-level compression unit 1, secondary compression unit 2, motor 3, one-level air entry 4, one-level exhaust outlet 5, secondary air entry 6, secondary exhaust outlet 7, each compression unit is respectively the discharge capacity of the discharge capacity of rotor-type compressor structure and secondary compression unit 2 less than one-level compression unit 1, and motor 3 drives one- level compression unit 1 and 2 operations of secondary compression unit by bent axle.Described secondary exhaust outlet 7 connects air cooler 8 successively, filter 9, electric expansion valve 10, evaporimeter 12, behind the gas-liquid separator 13, the one-level air entry 4 that connects compressor, described magnetic valve 11 is arranged between secondary air entry 6 and the evaporimeter 12, constitute low pressure Ps between described gas-liquid separator 13 and the one-level compression unit, press Pm in constituting between one-level compression unit and the secondary compression unit, behind the secondary compression unit high pressure P d, the low pressure Ps gas that comes from evaporator outlet enters the one-level compression unit by one-level air entry 4, after the one-level compression, form intermediate pressure Pm, the back is discharged to outside the housing by one-level steam vent 5, the medium pressure gas that one-level exhaust outlet 5 is discharged can directly enter secondary suction hole 6, or after cooling off by intercooler, enter secondary air entry 6, through after 2 compressions of secondary compression unit, form high pressure P d gas and also be discharged to enclosure interior again, after enter secondary exhaust outlet 7 and discharge.
Normal heat pump circulation time magnetic valve 11 cuts out, the gases at high pressure that secondary exhaust outlet 7 is discharged filter through air cooler 8 coolings, filter 9 successively, electric expansion valve 10 expands, evaporimeter 12 evaporates, gas-liquid separator 13 gas-liquid separations, returns the one-level air entry 4 of compressor; During defrost cycle, magnetic valve 11 is opened, electric expansion valve 10 standard-sized sheets, and the gas that one-level exhaust outlet 5 is discharged directly enters evaporimeter 12 evaporations by magnetic valve 11, enters one-level air entry 4 then after gas-liquid separator 13 separates, and adopts the one-level exhaust to defrost.
Between secondary exhaust outlet 7 and one-level exhaust outlet 5, be provided with check valve 14, the trend of this check valve 14 is that one-level exhaust outlet 5 is to secondary exhaust outlet 7, as the intermediate pressure Pm of compressor during greater than high side pressure Pd, check valve 14 is opened automatically, this moment intermediate pressure Pm and high side pressure Pd bypass, make the secondary compression unit be in idling conditions, thereby further improve two grade blade operation stabilities.
As shown in figure 10, the heat pump circulating system of two-stage rotor-type compressor and band pressure release defrosting, this system comprises compressor, air cooler 8, filter 9, electric expansion valve 10, four-way change-over valve 11 ', evaporimeter 12, gas-liquid separator 13, described compressor comprises one-level compression unit 1, secondary compression unit 2, motor 3, one-level air entry 4, one-level exhaust outlet 5, secondary air entry 6, secondary exhaust outlet 7, each compression unit is respectively the discharge capacity of the discharge capacity of rotor-type compressor structure and secondary compression unit 2 less than one-level compression unit 1, and motor 3 drives one- level compression unit 1 and 2 operations of secondary compression unit by bent axle.Described secondary exhaust outlet 7 connects air cooler 8 successively, filter 9, electric expansion valve 10, evaporimeter 12, behind the gas-liquid separator 13, the one-level air entry 4 that connects compressor, described four-way change-over valve 11 ' is arranged on described secondary exhaust outlet 7, evaporimeter 12, between air cooler 8 and the gas-liquid separator 13, constitute low pressure Ps between described gas-liquid separator 13 and the one-level compression unit, press Pm in constituting between one-level compression unit and the secondary compression unit, behind the secondary compression unit high pressure P d, the low pressure Ps gas that comes from evaporator outlet enters the one-level compression unit by one-level air entry 4, after the one-level compression, form intermediate pressure Pm, the back is discharged to outside the housing by one-level steam vent 5, the medium pressure gas that one-level exhaust outlet 5 is discharged can directly enter secondary suction hole 6, or after cooling off by intercooler, enter secondary air entry 6, through after 5 compressions of secondary compression unit, form high pressure P d gas and also be discharged to enclosure interior again, after enter secondary exhaust outlet 7 and discharge.
Normal heat pump circulation time, regulate four-way change-over valve 11 ', secondary exhaust outlet 7 is communicated with air cooler 8, evaporimeter 12 is communicated with gas-liquid separator 13, the gases at high pressure that secondary exhaust outlet 7 is discharged filter through air cooler 8 coolings, filter 9 successively, electric expansion valve 10 expands, evaporimeter 12 evaporates, gas-liquid separator 13 gas-liquid separations, returns the one-level air entry 4 of compressor; During defrost cycle, regulate four-way change-over valve 11 ', secondary exhaust outlet 7 is communicated with evaporimeter 12, air cooler 8 is communicated with gas-liquid separator 13, electric expansion valve 10 standard-sized sheets, the gas that one-level exhaust outlet 5 is discharged directly enters evaporimeter 12 evaporations by four-way change-over valve 11 ', enters one-level air entry 4 then after gas-liquid separator 13 separates, and adopts the secondary exhaust to defrost.
Between secondary exhaust outlet 7 and one-level exhaust outlet 5, be provided with check valve 14, the trend of this check valve 14 is that one-level exhaust outlet 5 is to secondary exhaust outlet 7, as the intermediate pressure Pm of compressor during greater than high side pressure Pd, check valve 14 is opened automatically, this moment intermediate pressure Pm and high side pressure Pd bypass, make the secondary compression unit be in idling conditions, thereby further improve two grade blade operation stabilities.
One-way valve mechanism can be installed in when phenomenon greater than high side pressure Pd appears in middle pressure P m, can make on any position that intermediate pressure Pm and high side pressure Pd connect, and therefore also can be installed in compressor inside.One-way valve mechanism also can be considered to be replaced by magnetic valve etc., by measuring the size of contrast Pm and Pd, controls the switch of magnetic valve, and when Pm＞Pd, magnetic valve is opened, when Pm＜Pd, and closed electromagnetic valve.
Claims (6)
1. the heat pump circulating system of two-stage rotor-type compressor and band pressure release and defrosting, this system comprises compressor, air cooler, filter, electric expansion valve, evaporimeter, gas-liquid separator, described compressor comprises the one-level compression unit, the secondary compression unit, the one-level air entry, the one-level exhaust outlet, the secondary air entry, the secondary exhaust outlet, described secondary exhaust outlet connects air cooler, air cooler connects filter successively, electric expansion valve, evaporimeter, behind the gas-liquid separator, the one-level air entry that connects compressor, constitute low pressure between described gas-liquid separator and the one-level compression unit, press in constituting between one-level compression unit and the secondary compression unit, it behind the secondary compression unit high pressure, it is characterized in that, also comprise communicating valve, it is inner or outside that this communicating valve is arranged on the compressor that low pressure is communicated with high pressure.
2. the heat pump circulating system of two-stage rotor-type compressor according to claim 1 and band pressure release defrosting is characterized in that described communicating valve is check valve or magnetic valve.
3. the heat pump circulating system of two-stage rotor-type compressor according to claim 1 and band pressure release and defrosting is characterized in that, described communicating valve one end connects the secondary exhaust outlet, and the other end connects the one-level exhaust outlet.
4. the heat pump circulating system of two-stage rotor-type compressor according to claim 1 and band pressure release and defrosting is characterized in that, is provided with magnetic valve between described secondary exhaust outlet and the evaporimeter.
5. the heat pump circulating system of two-stage rotor-type compressor according to claim 1 and band pressure release and defrosting is characterized in that, is provided with magnetic valve between described secondary air entry and the evaporimeter.
6. the heat pump circulating system of two-stage rotor-type compressor according to claim 1 and band pressure release and defrosting is characterized in that, is provided with four-way change-over valve between described secondary exhaust outlet, evaporimeter, air cooler and the gas-liquid separator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202045292U CN201772684U (en) | 2010-05-24 | 2010-05-24 | Two-stage rotor type compressor and decompression and defrosting heat pump circulation system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202045292U CN201772684U (en) | 2010-05-24 | 2010-05-24 | Two-stage rotor type compressor and decompression and defrosting heat pump circulation system |
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| CN201772684U true CN201772684U (en) | 2011-03-23 |
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| CN2010202045292U Expired - Lifetime CN201772684U (en) | 2010-05-24 | 2010-05-24 | Two-stage rotor type compressor and decompression and defrosting heat pump circulation system |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104848617A (en) * | 2015-06-08 | 2015-08-19 | 上海海立睿能环境技术有限公司 | Defrosting system of carbon dioxide heat pump water heater |
| CN108591059A (en) * | 2018-06-19 | 2018-09-28 | 广东美芝制冷设备有限公司 | Compression set and refrigeration system with it |
| CN113091182A (en) * | 2021-05-24 | 2021-07-09 | 青岛腾远设计事务所有限公司 | Full fresh air direct expansion type air handling unit and air conditioning system |
| CN113340031A (en) * | 2021-05-27 | 2021-09-03 | 广东芬尼克兹节能设备有限公司 | CO (carbon monoxide)2Control method for heat pump system, control system for heat pump system, and storage medium |
-
2010
- 2010-05-24 CN CN2010202045292U patent/CN201772684U/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104848617A (en) * | 2015-06-08 | 2015-08-19 | 上海海立睿能环境技术有限公司 | Defrosting system of carbon dioxide heat pump water heater |
| CN108591059A (en) * | 2018-06-19 | 2018-09-28 | 广东美芝制冷设备有限公司 | Compression set and refrigeration system with it |
| CN113091182A (en) * | 2021-05-24 | 2021-07-09 | 青岛腾远设计事务所有限公司 | Full fresh air direct expansion type air handling unit and air conditioning system |
| CN113340031A (en) * | 2021-05-27 | 2021-09-03 | 广东芬尼克兹节能设备有限公司 | CO (carbon monoxide)2Control method for heat pump system, control system for heat pump system, and storage medium |
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Granted publication date: 20110323 |
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| CX01 | Expiry of patent term |