US20070113583A1 - Compressor for refrigeratory equipment - Google Patents
Compressor for refrigeratory equipment Download PDFInfo
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- US20070113583A1 US20070113583A1 US11/600,638 US60063806A US2007113583A1 US 20070113583 A1 US20070113583 A1 US 20070113583A1 US 60063806 A US60063806 A US 60063806A US 2007113583 A1 US2007113583 A1 US 2007113583A1
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- Prior art keywords
- cooling
- compressor
- refrigeratory
- casing
- equipment
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/006—Cooling of compressor or motor
- F25B31/008—Cooling of compressor or motor by injecting a liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
- F04B39/062—Cooling by injecting a liquid in the gas to be compressed
Definitions
- the present invention relates to a refrigeratory equipment and its compressor. More particularly, the refrigeratory equipment can absorb and dissipate the mechanical heat produced by the compressor.
- the conventional refrigeratory equipment comprises several components.
- the compressor the refrigerant is compressed and converted into a high pressure and high temperature gas. Once compressed, the hot refrigerant is then discharged into a condenser and converted into a low temperature liquid state. After that, the pressure of the liquid refrigerant is decreased and the liquid refrigerant is converted into the gas refrigerant by a pressure releaser which is usually a capillary or an expansion salve.
- a pressure releaser which is usually a capillary or an expansion salve.
- the refrigerant is cooled, it is then delivered into a evaporator wherein the evaporation of the refrigerant is the cause of the decrease of the temperature.
- what exchanges heat energy with the evaporator is room air.
- the reciprocating compressor uses a motor driven crankshaft to drive internal pistons.
- the compression of the refrigerant is driven by a rotor in the compressor.
- frictional heat is generated in all these mechanical devices and the electromotor produces heat itself too.
- heat energy is dispersed by the refrigerant which functions as the cooling fluid, the heat energy causes temperature of the gas refrigerant to rise even up to 150° C. Hence, more energy has to be consumed to condense the refrigerant after heat is absorbed at compressor, and therefore the efficiency of the compressor is quite low.
- the inventors provide a refrigeratory equipment and its compressor to effectively overcome the demerit that there is no way to disperse the mechanical heat generated in the compressor existing in the prior art.
- a refrigeratory equipment comprising a compressor having a casing and a compressing device contained in the casing, a condenser connected with the compressor for condensing a refrigerant coming from the compressor, an expansion valve connected with the condenser for expanding the refrigerant condensed by the condenser, an evaporator connected with both the expansion valve and the compressor wherein the refrigerant coming from the expansion salve is evaporated for absorbing a heat and the evaporated refrigerant is transported to the compressor to be compressed, and a cooling pipeline connected with the casing and having a cool liquid flowing therein to absorb and to dissipate a heat from the compressor.
- the cooling pipeline further comprises an outer section outside of the casing and an inner section inside of the casing.
- the outer section is further connected with a heater so as to heat a substance by the heater.
- the substance is water.
- the cooling pipeline is further connected with an auxiliary cooling pipeline and a rotary cooling pipeline for cooling a substance in the cooling pipeline.
- a compressor configuration for a refrigeratory equipment comprises a casing having a compressing device mounted therein and a cooling pipe passing through the casing for cooling the compressing device.
- the cooling pipe comprises an outer section outside of the casing and an inner section inside of the casing.
- the inner section includes a plurality of manifolds.
- the compressor configuration further comprises a fin disposed between the manifolds.
- the cooling pipe is connected with a heater wherein the heater uses a heat absorbed by the cooling pipe for heating.
- the cooling pipe is further connected with a condenser for condensing a refrigerant, a pressure releaser and an evaporator, wherein the cooling pipe is connected with the condenser for introducing the refrigerant condensed by the condenser into the casing.
- the pressure releaser is an expansion valve.
- a compressor configuration for a refrigeratory equipment comprises a compressing device having a first cooling channel for cooling the compressing device, an electromotor having a second cooling channel connected to the first cooling channel for cooling the electromotor, wherein a heat generated from both the compressing device and the electromotor is dissipated from the compressor configuration.
- the compressor configuration further comprises a cooling device connected with the first and the second cooling channels, wherein the cooling device has a working fluid circulating between an inside of the compressing configuration and the cooling device, wherein the working fluid absorbs a heat at the first and the second cooling channels and is further cooled at the cooling device.
- the cooling device further comprises a first auxiliary cooling pipeline for cooling the working fluid coming from the compressor configuration and a second auxiliary cooling pipeline for cooling the working fluid coming from the first auxiliary cooling pipeline.
- the second auxiliary cooling pipeline is a rotary cooling pipe.
- the rotary cooling pipe is a rotating heat pipe.
- FIG. 1 is a diagram showing the compressor used for the refrigeratory equipment according to the present invention
- FIG. 2 is an embodiment according to the present invention.
- FIG. 3 is another embodiment according to the present invention.
- FIG. 4 is an embodiment of the refrigeratory equipment according to the present invention.
- FIG. 5 is another embodiment of the refrigeratory equipment according to the present invention.
- the present invention proposes a compressor for the refrigeratory equipment. To achieve the purpose of improving the efficiency of the compressor, cooling outside and inside of the compressor is focused.
- FIG. 1 is a diagram showing the compressor used for the refrigeratory equipment according to the present invention.
- a compressor 1 comprises an electromotor 12 and a compressing device 10 .
- FIG. 1 is illustrated with a rotary compressor, but the type of compressor can be varied.
- the electromotor 12 drives a rotor 100 in the compressing device 10 via a transmission shaft 120 to compress a refrigerant.
- a first cooling channel 31 is installed in the compressing device 10 and a second cooling channel 32 is installed in the electromotor 12 .
- the effect of taking away the heat energy generated by the compressing device 10 or the electromotor 12 is achieved by a working fluid flowing in the first cooling channel 31 and the second cooling channel 32 .
- the compressor has a casing 13 for containing the compressing device 10 and the electromotor 12 .
- the first and the second cooling channels 31 , 32 are also contained in the casing 13 , so they are called the inner section as well.
- a first outer section 33 a and a second outer section 33 b are outside of the casing 13 , wherein they are used to introduce the working fluid into the refrigeratory equipment and introduce the working fluid coming from the refrigeratory equipment into the casing 13 again.
- the working fluid which flows through the first outer section 33 a to the casing 13 arrives a first circular section 30 a first. It is because that in order to have better cooling effect, there are a plurality of the first cooling channels 31 .
- the working fluid is distributed to each first cooling channel 31 via the first circular section 30 a connected to the first outer section 33 a .
- the working fluid then flows to the second cooling channel 32 which usually directly takes the heat generated from the electromotor 12 away by passing through a silicon steel-sheet 121 of the electromotor 12 .
- the number and the size between the first and the second cooling channels 31 , 32 can be different, which depends on the actual necessity of the compressor.
- the working fluid coming from the second cooling channel 32 is converged at a second circular section 30 b and then flows to a second outer section 33 b .
- the aforementioned working fluid passes the first cooling channel 31 first and then the second cooling channel 32 ; however it can flow in opposite direction, which depends on the actual necessity of the compressor as well.
- the working fluid can flow from lower temperature devices to higher temperature ones in principle.
- the second outer section is further connected to a cooling device. After the working, fluid is cooled in the cooling device, it flows back into the compressor configuration again.
- a fin 310 is configured outside of the first cooling channel 31 to increase the heat exchanging area.
- FIG. 2 is an embodiment according to the present invention, wherein the compressor 1 is covered by a shell 5 .
- a cooling space 30 formed between the compressor 1 and the shell 5 is connected to the cooling device 4 by the first outer section 33 a and the second outer section 33 b .
- the cooling device 4 is used to cool the compressor 1 via introducing a working fluid coming from the first outer section 33 a into the cooling space 30 , where the working fluid absorbs heat generated from the compressor 1 , and then the-working fluid is discharged from the space via the second outer section 33 b and flows back to the cooling device 4 .
- the heat absorbed from the compressor 1 is taken away in the cooling device 4 , and then the cooled working fluid is introduced into the cooling space 30 again and moves in circles for cooling the compressor 1 .
- FIG. 3 is another embodiment according to the present invention.
- the embodiment of FIG. 3 is advantageous to reduce the volume of the compressor, because the embodiment of FIG. 2 occupies more space.
- An outer cooling pipeline 8 wraps around the outside of the compressor 1 .
- the working fluid which is used to cool the compressor 1 , enters an entry 81 a of the outer cooling pipeline 8 and is discharged from an exit 81 b.
- Both the two outer sections are connected to the cooling device 4 , as shown in FIG. 2 .
- FIG. 4 shows an embodiment of the refrigeratory equipment according to the present invention.
- the refrigeratory equipment cormprises a compressor 1 .
- the high pressure and high temperature refrigerant is delivered into a condenser 6 a by a first pipe 7 a and converted into a low temperature liquid state.
- the reprigerant is further delivered into a pressure releaser 6 b by a second pipe 7 b .
- the pressure of the liquid refrigerant is reduced by the pressure releaser 6 b which is usually a capillary or an expansion salve.
- the refrigerant is then delivered into a evaporator 6 c by a third pipe 7 c .
- the evaporator 6 c is usually a type of heat exchanger. If the refrigeratory equipment is an air conditioner, then the evaporator 6 c that functions as a heat exchanger exchanges heat with room air to reduce room temperature. The temperature of the refrigerant in the evaporator 6 c will rise and the refrigerant will be delivered back to the compressor 1 by a fourth pipe finally. Concering the second pipe 7 b , a shunt 7 b ′ is designed in the present invention for collecting part of the working fluid to cool the compressor 1 . Therefore, the shunt 7 b ′ is a tool for the entry of the working fluid into a cooling device of a compressor configuration 3 ′.
- the shunt 7 b ′ can be connected to the first outer section 33 a , as shown in FIG. 1 . Reffering to FIG. 1 , the mechanical and electricalal heat generated from the compressor 1 will be taken away by the first and the second cooling channels 31 , 32 in the compressor 1 . Therefor, the first and the second cooling channels 31 , 32 in FIG. 1 constitute the cooling device of the compressor configuration 3 ′ in FIG. 4 . Moreover, the shunt 7 b ′ can be connected to the first outer section 33 a , as shown in FIG. 2 , and leads the working fluid into the cooling space 30 for cooling the compressor 1 . Thus, the cooling space 30 in FIG. 2 constitutes the cooling device of the compressor configuration 3 ′ in FIG. 4 .
- the shunt 7 b ′ can be connected to the entry 81 a of the outer cooling pipeline 8 , as shown in FIG. 3 , for cooling the compressor 1 . Therefore, the outer cooling pipeline 8 in FIG. 3 constitutes the cooling device of the compressor configuration 3 ′ in FIG. 4 .
- the compressed working fluid which is a refrigerant
- the condenser 6 a After the working fluid enters the cooling device of the compressor configuration 3 ′, the compressed working fluid, which is a refrigerant, then enters the condenser 6 a . Accordingly, working fluid circles in the cooling device of the compressor configuration 3 ′ are formed.
- FIG. 5 shows another embodiment of the refrigeratory equipment according to the present invention.
- the refrigeratory equipment comprises a compressor 1 .
- the refrigerant is compressed, it is then discharged into a condenser 6 a by the first pipe 7 a , and the high pressure and high temperature refrigerant will be condensed into a low temperature liquid state.
- the reprigerant is further delivered into a pressure releaser 6 b by the second pipe 7 b .
- the pressure of the liquid refrigerant is decreased by the pressure releaser 6 b which is usually a capillary or an expansion salve.
- the refrigerant is then delivered into a evaporator 6 c by the third pipe 7 c .
- the evaporator 6 c is usually a type of heat exchanger. If the refrigeratory equipment is an air conditioner, the evaporator 6 c that functions as a heat exchanger exchanges heat with room air to reduce room temperature. The temperature of the refrigerant in the evaporator 6 c will rise and the refrigerant will be delivered back to the compressor 1 by a fourth pipe finally.
- the characteristic of the embodiment of FIG. 5 lies in a cooling device 4 for cooling the compressor 1 .
- the cooling device 4 comprises a refrigeratory 40 and a cooling pipe that includes a first cooling pipe 4 a , a second cooling pipe 4 b and a third cooling pipe 4 c .
- the refrigeratory 40 will introduce a cooled working fluid into the compressor 1 by the third cooling pipe 4 c .
- the refrigeratory 40 After the working fluid absorbs the mechanical and electrical heat generated from the compressor 1 , it will be delivered back to the refrigeratory 40 by the first cooling pipe 4 a for cooling.
- the refrigeratory 40 is a heat exchanger such as an air-cooled or a water-cooled heat exchanger.
- the refrigeratory 40 comprises a cooling loop pipe 41 and a rotating heat pipe 42 for increasing the cooling efficiency.
- the cooling loop pipe 41 can be a shell and tube heat exchanger, a plate heat exchanger, an air-cooled cooling tower, or a cooling tower.
- the cooling device 4 is used to cool the compressor 1 , it is connected to the first outer section 33 a and the second outer section 33 b . That is to say, the third cooling channel 4 c is connected to the first outer section 33 a , and the first cooling channel 4 a is connected to the second outer section 33 b .
- the working fluid absorbs mechanical and electrical heat generated by the compressor 1 .
- the working fluid is delivered from the compressor 1 via the interconnected first cooling channel 4 a and second outer section 33 b to the cooling device 4 .
- the cooling device 4 is used to cool the compressor 1 , it is connected to the first outer section 33 a and the second outer section 33 b . That is to say, the third cooling channel 4 c is connected to the first outer section 33 a , and the first cooling channel 4 a is connected to the second outer section 33 b .
- the working fluid is cooled by the cooling device 4 , it is then introduced into the cooling space 30 formed between the compressor 1 and the shell 5 by the interconnected third cooling channel 4 c and first outer section 33 a .
- the working fluid exchanges heat with the compressor 1 , it is discharged from the cooling space 30 via the second outer section 33 b and enters the cooling device 4 again via the first cooling channel 4 a.
- the cooling device 4 is used to cool the compressor 1 , the working fluid that is cooled by the cooling device 4 will enter the entry 81 a as shown in FIG. 3 , pass the outer cooling pipeline 8 , and then is discharged from the exit 81 b. Therefore, the entry 81 a is connected to the third cooling channel 4 c in FIG. 5 , and the exit 81 b is connected to the first cooling channel 4 a in FIG. 5 . Accordingly, a cooling loop for cooling the compressor is formed.
- the characteristic of the present invention lies in the cooling for the compressor.
- the reason for cooling the compressor is that mechanical elements for compressing the refrigerant in the compressor and the electromotor used to drive the mechanical elements all generate heat. The heat leads to the decrease in the efficiency of the compressor.
- the present invention proposes a configuration for cooling the compressor to solve the mentioned problem.
- the compressor will be efficiently cooled by the cooling channel that is inside of the compressor as shown in FIG. 1 , or the cooling space formed outside of the compressor as shown in FIG. 2 , or the cooling pipeline configured outside of the compressor as shown in FIG. 3 .
- the operating system of the refrigeratory equipment that possesses the function of cooling the compressor is illustrated in FIG. 4 and FIG. 5 , wherein the working fluid of the refrigeratory equipment itself is used to cool the compressor in FIG. 4 , and an independent cycle is used to cool the compressor in FIG. 5 .
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Abstract
Description
- The present invention relates to a refrigeratory equipment and its compressor. More particularly, the refrigeratory equipment can absorb and dissipate the mechanical heat produced by the compressor.
- The conventional refrigeratory equipment comprises several components. In the compressor, the refrigerant is compressed and converted into a high pressure and high temperature gas. Once compressed, the hot refrigerant is then discharged into a condenser and converted into a low temperature liquid state. After that, the pressure of the liquid refrigerant is decreased and the liquid refrigerant is converted into the gas refrigerant by a pressure releaser which is usually a capillary or an expansion salve. When the refrigerant is cooled, it is then delivered into a evaporator wherein the evaporation of the refrigerant is the cause of the decrease of the temperature. For air conditioners, what exchanges heat energy with the evaporator is room air.
- There are two major devices in the compressor. One is a electromotor and the other is a compressor drived by the electromotor. The reciprocating compressor uses a motor driven crankshaft to drive internal pistons. For the rotary compressor and the scroll compressor, the compression of the refrigerant is driven by a rotor in the compressor. However, frictional heat is generated in all these mechanical devices and the electromotor produces heat itself too. Although in the compressor heat energy is dispersed by the refrigerant which functions as the cooling fluid, the heat energy causes temperature of the gas refrigerant to rise even up to 150° C. Hence, more energy has to be consumed to condense the refrigerant after heat is absorbed at compressor, and therefore the efficiency of the compressor is quite low. Otherwise, though there is lubricant between the ring and rotor and in the bearing of the compressor and the electromotor, it absorbs heat when the compressor and the electromotor work. There is no specific heat sink for lubricant, so it has no way to disperse its heat energy.
- Therefore, because of the defect in the prior art, the inventors provide a refrigeratory equipment and its compressor to effectively overcome the demerit that there is no way to disperse the mechanical heat generated in the compressor existing in the prior art.
- In accordance with an aspect of the present invention, a refrigeratory equipment is provided. The refrigeratory equipment comprises a compressor having a casing and a compressing device contained in the casing, a condenser connected with the compressor for condensing a refrigerant coming from the compressor, an expansion valve connected with the condenser for expanding the refrigerant condensed by the condenser, an evaporator connected with both the expansion valve and the compressor wherein the refrigerant coming from the expansion salve is evaporated for absorbing a heat and the evaporated refrigerant is transported to the compressor to be compressed, and a cooling pipeline connected with the casing and having a cool liquid flowing therein to absorb and to dissipate a heat from the compressor.
- Preferably, the cooling pipeline further comprises an outer section outside of the casing and an inner section inside of the casing.
- Preferably, the outer section is further connected with a heater so as to heat a substance by the heater.
- Preferably, the substance is water.
- Preferably, the cooling pipeline is further connected with an auxiliary cooling pipeline and a rotary cooling pipeline for cooling a substance in the cooling pipeline.
- In accordance with another aspect of the present invention, a compressor configuration for a refrigeratory equipment is provided. The compressor configuration comprises a casing having a compressing device mounted therein and a cooling pipe passing through the casing for cooling the compressing device.
- Preferably, the cooling pipe comprises an outer section outside of the casing and an inner section inside of the casing.
- Preferably, the inner section includes a plurality of manifolds.
- Preferably, the compressor configuration further comprises a fin disposed between the manifolds.
- Preferably, the cooling pipe is connected with a heater wherein the heater uses a heat absorbed by the cooling pipe for heating.
- Preferably, the cooling pipe is further connected with a condenser for condensing a refrigerant, a pressure releaser and an evaporator, wherein the cooling pipe is connected with the condenser for introducing the refrigerant condensed by the condenser into the casing.
- Preferably, the pressure releaser is an expansion valve.
- In accordance with a further aspect of the present invention, a compressor configuration for a refrigeratory equipment is provided. The compressor configuration comprises a compressing device having a first cooling channel for cooling the compressing device, an electromotor having a second cooling channel connected to the first cooling channel for cooling the electromotor, wherein a heat generated from both the compressing device and the electromotor is dissipated from the compressor configuration.
- Preferably, the compressor configuration further comprises a cooling device connected with the first and the second cooling channels, wherein the cooling device has a working fluid circulating between an inside of the compressing configuration and the cooling device, wherein the working fluid absorbs a heat at the first and the second cooling channels and is further cooled at the cooling device.
- Preferably, the cooling device further comprises a first auxiliary cooling pipeline for cooling the working fluid coming from the compressor configuration and a second auxiliary cooling pipeline for cooling the working fluid coming from the first auxiliary cooling pipeline.
- Preferably, the second auxiliary cooling pipeline is a rotary cooling pipe.
- Preferably, the rotary cooling pipe is a rotating heat pipe.
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FIG. 1 is a diagram showing the compressor used for the refrigeratory equipment according to the present invention; -
FIG. 2 is an embodiment according to the present invention; -
FIG. 3 is another embodiment according to the present invention; -
FIG. 4 is an embodiment of the refrigeratory equipment according to the present invention; and -
FIG. 5 is another embodiment of the refrigeratory equipment according to the present invention. - In order to solve the problem of the low efficiency of the conventional compressor, the present invention proposes a compressor for the refrigeratory equipment. To achieve the purpose of improving the efficiency of the compressor, cooling outside and inside of the compressor is focused.
- Please refer to
FIG. 1 , which is a diagram showing the compressor used for the refrigeratory equipment according to the present invention. As shown, acompressor 1 comprises anelectromotor 12 and acompressing device 10. AlthoughFIG. 1 is illustrated with a rotary compressor, but the type of compressor can be varied. Theelectromotor 12 drives arotor 100 in thecompressing device 10 via a transmission shaft 120 to compress a refrigerant. For achieving the purpose of taking away the heat generated by thecompressor 1, afirst cooling channel 31 is installed in thecompressing device 10 and asecond cooling channel 32 is installed in theelectromotor 12. The effect of taking away the heat energy generated by thecompressing device 10 or theelectromotor 12 is achieved by a working fluid flowing in thefirst cooling channel 31 and thesecond cooling channel 32. - Please refer to
FIG. 1 again. The compressor has acasing 13 for containing thecompressing device 10 and theelectromotor 12. The first and thesecond cooling channels casing 13, so they are called the inner section as well. A first outer section 33 a and a secondouter section 33 b are outside of thecasing 13, wherein they are used to introduce the working fluid into the refrigeratory equipment and introduce the working fluid coming from the refrigeratory equipment into thecasing 13 again. Before arriving thefirst cooling channel 31, the working fluid which flows through the first outer section 33 a to thecasing 13 arrives a firstcircular section 30 a first. It is because that in order to have better cooling effect, there are a plurality of thefirst cooling channels 31. The working fluid is distributed to eachfirst cooling channel 31 via the firstcircular section 30 a connected to the first outer section 33 a. The working fluid then flows to thesecond cooling channel 32 which usually directly takes the heat generated from theelectromotor 12 away by passing through a silicon steel-sheet 121 of theelectromotor 12. Of course the number and the size between the first and thesecond cooling channels second cooling channel 32 is converged at a secondcircular section 30 b and then flows to a secondouter section 33 b. The aforementioned working fluid passes thefirst cooling channel 31 first and then thesecond cooling channel 32; however it can flow in opposite direction, which depends on the actual necessity of the compressor as well. The working fluid can flow from lower temperature devices to higher temperature ones in principle. The second outer section is further connected to a cooling device. After the working, fluid is cooled in the cooling device, it flows back into the compressor configuration again. In addition, in order to increase the rate of heat exchange, afin 310 is configured outside of thefirst cooling channel 31 to increase the heat exchanging area. -
FIG. 2 is an embodiment according to the present invention, wherein thecompressor 1 is covered by ashell 5. A cooling space 30 formed between thecompressor 1 and theshell 5 is connected to thecooling device 4 by the first outer section 33 a and the secondouter section 33 b. Thecooling device 4 is used to cool thecompressor 1 via introducing a working fluid coming from the first outer section 33 a into the cooling space 30, where the working fluid absorbs heat generated from thecompressor 1, and then the-working fluid is discharged from the space via the secondouter section 33 b and flows back to thecooling device 4. The heat absorbed from thecompressor 1 is taken away in thecooling device 4, and then the cooled working fluid is introduced into the cooling space 30 again and moves in circles for cooling thecompressor 1. -
FIG. 3 is another embodiment according to the present invention. The embodiment ofFIG. 3 is advantageous to reduce the volume of the compressor, because the embodiment ofFIG. 2 occupies more space. Anouter cooling pipeline 8 wraps around the outside of thecompressor 1. The working fluid, which is used to cool thecompressor 1, enters an entry 81 a of theouter cooling pipeline 8 and is discharged from anexit 81 b. Both the two outer sections are connected to thecooling device 4, as shown inFIG. 2 . Please refer toFIG. 2 for the functions of thecooling device 4. - Please refer to
FIG. 4 , which shows an embodiment of the refrigeratory equipment according to the present invention. As shown, the refrigeratory equipment cormprises acompressor 1. After compressing a refrigerant, the high pressure and high temperature refrigerant is delivered into a condenser 6 a by a first pipe 7 a and converted into a low temperature liquid state. After that, the reprigerant is further delivered into apressure releaser 6 b by asecond pipe 7 b. The pressure of the liquid refrigerant is reduced by thepressure releaser 6 b which is usually a capillary or an expansion salve. Furthermore, the refrigerant is then delivered into aevaporator 6 c by athird pipe 7 c. Theevaporator 6 c is usually a type of heat exchanger. If the refrigeratory equipment is an air conditioner, then theevaporator 6 c that functions as a heat exchanger exchanges heat with room air to reduce room temperature. The temperature of the refrigerant in theevaporator 6 c will rise and the refrigerant will be delivered back to thecompressor 1 by a fourth pipe finally. Concering thesecond pipe 7 b, ashunt 7 b′ is designed in the present invention for collecting part of the working fluid to cool thecompressor 1. Therefore, theshunt 7 b′ is a tool for the entry of the working fluid into a cooling device of acompressor configuration 3′. Theshunt 7 b′ can be connected to the first outer section 33 a, as shown inFIG. 1 . Reffering toFIG. 1 , the mechanical and electricalal heat generated from thecompressor 1 will be taken away by the first and thesecond cooling channels compressor 1. Therefor, the first and thesecond cooling channels FIG. 1 constitute the cooling device of thecompressor configuration 3′ inFIG. 4 . Moreover, theshunt 7 b′ can be connected to the first outer section 33 a, as shown inFIG. 2 , and leads the working fluid into the cooling space 30 for cooling thecompressor 1. Thus, the cooling space 30 inFIG. 2 constitutes the cooling device of thecompressor configuration 3′ inFIG. 4 . Furthermore, theshunt 7 b′ can be connected to the entry 81 a of theouter cooling pipeline 8, as shown inFIG. 3 , for cooling thecompressor 1. Therefore, theouter cooling pipeline 8 inFIG. 3 constitutes the cooling device of thecompressor configuration 3′ inFIG. 4 . - Please refer to
FIG. 4 again. After the working fluid enters the cooling device of thecompressor configuration 3′, the compressed working fluid, which is a refrigerant, then enters the condenser 6 a. Accordingly, working fluid circles in the cooling device of thecompressor configuration 3′ are formed. - Please refer to
FIG. 5 , which shows another embodiment of the refrigeratory equipment according to the present invention. The refrigeratory equipment comprises acompressor 1. Once the refrigerant is compressed, it is then discharged into a condenser 6 a by the first pipe 7 a, and the high pressure and high temperature refrigerant will be condensed into a low temperature liquid state. After that, the reprigerant is further delivered into apressure releaser 6 b by thesecond pipe 7 b. The pressure of the liquid refrigerant is decreased by thepressure releaser 6 b which is usually a capillary or an expansion salve. Furthermore, the refrigerant is then delivered into aevaporator 6 c by thethird pipe 7 c. Theevaporator 6 c is usually a type of heat exchanger. If the refrigeratory equipment is an air conditioner, theevaporator 6 c that functions as a heat exchanger exchanges heat with room air to reduce room temperature. The temperature of the refrigerant in theevaporator 6 c will rise and the refrigerant will be delivered back to thecompressor 1 by a fourth pipe finally. However, the characteristic of the embodiment ofFIG. 5 lies in acooling device 4 for cooling thecompressor 1. Thecooling device 4 comprises a refrigeratory 40 and a cooling pipe that includes afirst cooling pipe 4 a, asecond cooling pipe 4 b and athird cooling pipe 4 c. The refrigeratory 40 will introduce a cooled working fluid into thecompressor 1 by thethird cooling pipe 4 c. After the working fluid absorbs the mechanical and electrical heat generated from thecompressor 1, it will be delivered back to the refrigeratory 40 by thefirst cooling pipe 4 a for cooling. In respect of the refrigeratory 40, it is a heat exchanger such as an air-cooled or a water-cooled heat exchanger. Furthermore, the refrigeratory 40 comprises a cooling loop pipe 41 and arotating heat pipe 42 for increasing the cooling efficiency. Besides, the cooling loop pipe 41 can be a shell and tube heat exchanger, a plate heat exchanger, an air-cooled cooling tower, or a cooling tower. - Please refer to
FIG. 5 andFIG. 1 again. Because thecooling device 4 is used to cool thecompressor 1, it is connected to the first outer section 33 a and the secondouter section 33 b. That is to say, thethird cooling channel 4 c is connected to the first outer section 33 a, and thefirst cooling channel 4 a is connected to the secondouter section 33 b. Hence, after the working fluid is cooled by thecooling device 4, it is then introduced into thecompressor 1 by the interconnectedthird cooling channel 4 c and first outer section 33 a. In the first andsecond cooling channels compressor 1. Then, the working fluid is delivered from thecompressor 1 via the interconnectedfirst cooling channel 4 a and secondouter section 33 b to thecooling device 4. - Please refer to
FIG. 5 andFIG. 2 again. Because thecooling device 4 is used to cool thecompressor 1, it is connected to the first outer section 33 a and the secondouter section 33 b. That is to say, thethird cooling channel 4 c is connected to the first outer section 33 a, and thefirst cooling channel 4 a is connected to the secondouter section 33 b. Thus, after the working fluid is cooled by thecooling device 4, it is then introduced into the cooling space 30 formed between thecompressor 1 and theshell 5 by the interconnectedthird cooling channel 4 c and first outer section 33 a. After the working fluid exchanges heat with thecompressor 1, it is discharged from the cooling space 30 via the secondouter section 33 b and enters thecooling device 4 again via thefirst cooling channel 4 a. - Please refer to
FIG. 5 andFIG. 3 again. Because thecooling device 4 is used to cool thecompressor 1, the working fluid that is cooled by thecooling device 4 will enter the entry 81 a as shown inFIG. 3 , pass theouter cooling pipeline 8, and then is discharged from theexit 81 b. Therefore, the entry 81 a is connected to thethird cooling channel 4 c inFIG. 5 , and theexit 81 b is connected to thefirst cooling channel 4 a inFIG. 5 . Accordingly, a cooling loop for cooling the compressor is formed. - Therefore, according to the aforementioned embodiments, the characteristic of the present invention lies in the cooling for the compressor. The reason for cooling the compressor is that mechanical elements for compressing the refrigerant in the compressor and the electromotor used to drive the mechanical elements all generate heat. The heat leads to the decrease in the efficiency of the compressor. Hence, the present invention proposes a configuration for cooling the compressor to solve the mentioned problem. The compressor will be efficiently cooled by the cooling channel that is inside of the compressor as shown in
FIG. 1 , or the cooling space formed outside of the compressor as shown inFIG. 2 , or the cooling pipeline configured outside of the compressor as shown inFIG. 3 . The operating system of the refrigeratory equipment that possesses the function of cooling the compressor is illustrated inFIG. 4 andFIG. 5 , wherein the working fluid of the refrigeratory equipment itself is used to cool the compressor inFIG. 4 , and an independent cycle is used to cool the compressor inFIG. 5 . - While the invention has been described in terms of what is presently considered to be the most practical and preferred embodiments, it is to be understood that the invention needs not be limited to the disclose embodiments. Therefore, it is intended to cover various modifications and similar arrangements included within the spirit and scope of the appended claims, which are to be accorded with the broadest interpretation so as to encompass all such modifications and similar structures.
Claims (19)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
TW094140856 | 2005-11-21 | ||
TW094140856A TWI298365B (en) | 2005-11-21 | 2005-11-21 | Compressor for refrigerator equipment |
Publications (1)
Publication Number | Publication Date |
---|---|
US20070113583A1 true US20070113583A1 (en) | 2007-05-24 |
Family
ID=38052143
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/600,638 Abandoned US20070113583A1 (en) | 2005-11-21 | 2006-11-16 | Compressor for refrigeratory equipment |
Country Status (2)
Country | Link |
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US (1) | US20070113583A1 (en) |
TW (1) | TWI298365B (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20120060538A1 (en) * | 2009-05-26 | 2012-03-15 | Mitsubishi Electric Corporation | Heat pump apparatus |
US8985517B2 (en) | 2012-10-26 | 2015-03-24 | Textron Innovations Inc. | Passive cooling of transmission using mast mounted heat pipes |
WO2015192629A1 (en) * | 2014-06-20 | 2015-12-23 | 珠海格力电器股份有限公司 | Capacity-variable compressor and control method thereof, capacity-variable unit and air conditioner |
US9272777B2 (en) | 2012-10-26 | 2016-03-01 | Textron Innovations Inc. | Helicopter gearbox auxiliary cooling system |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
TW201317458A (en) * | 2011-10-18 | 2013-05-01 | yi-nan Gao | High-speed tornado swirling centrifugal pipe device |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4049410A (en) * | 1974-07-29 | 1977-09-20 | Allan Sinclair Miller | Gas compressors |
US4201523A (en) * | 1978-01-23 | 1980-05-06 | Olofsson Bjorn O E | Device for cooling and silencing of noise of a compressor or vacuum pump |
US20030094007A1 (en) * | 2001-11-20 | 2003-05-22 | Lg Electronics Inc. | Cooling system and cooling method |
US7334428B2 (en) * | 2005-09-30 | 2008-02-26 | Sullair Corporation | Cooling system for a rotary screw compressor |
-
2005
- 2005-11-21 TW TW094140856A patent/TWI298365B/en not_active IP Right Cessation
-
2006
- 2006-11-16 US US11/600,638 patent/US20070113583A1/en not_active Abandoned
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4049410A (en) * | 1974-07-29 | 1977-09-20 | Allan Sinclair Miller | Gas compressors |
US4201523A (en) * | 1978-01-23 | 1980-05-06 | Olofsson Bjorn O E | Device for cooling and silencing of noise of a compressor or vacuum pump |
US20030094007A1 (en) * | 2001-11-20 | 2003-05-22 | Lg Electronics Inc. | Cooling system and cooling method |
US7334428B2 (en) * | 2005-09-30 | 2008-02-26 | Sullair Corporation | Cooling system for a rotary screw compressor |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20120060538A1 (en) * | 2009-05-26 | 2012-03-15 | Mitsubishi Electric Corporation | Heat pump apparatus |
US8973384B2 (en) * | 2009-05-26 | 2015-03-10 | Mitsubishi Electric Corporation | Heat pump apparatus |
US8985517B2 (en) | 2012-10-26 | 2015-03-24 | Textron Innovations Inc. | Passive cooling of transmission using mast mounted heat pipes |
US9272777B2 (en) | 2012-10-26 | 2016-03-01 | Textron Innovations Inc. | Helicopter gearbox auxiliary cooling system |
WO2015192629A1 (en) * | 2014-06-20 | 2015-12-23 | 珠海格力电器股份有限公司 | Capacity-variable compressor and control method thereof, capacity-variable unit and air conditioner |
Also Published As
Publication number | Publication date |
---|---|
TWI298365B (en) | 2008-07-01 |
TW200720541A (en) | 2007-06-01 |
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