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WO2013011523A1 - Compresseur destiné à produire une compression écoénergétique - Google Patents

Compresseur destiné à produire une compression écoénergétique Download PDF

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Publication number
WO2013011523A1
WO2013011523A1 PCT/IN2012/000495 IN2012000495W WO2013011523A1 WO 2013011523 A1 WO2013011523 A1 WO 2013011523A1 IN 2012000495 W IN2012000495 W IN 2012000495W WO 2013011523 A1 WO2013011523 A1 WO 2013011523A1
Authority
WO
WIPO (PCT)
Prior art keywords
operating
compressor
driven shaft
shaft
compression cylinders
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/IN2012/000495
Other languages
English (en)
Inventor
Dhananjay SHARMA
Arun Anand
Ajay Raina
Vijay Jain
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO2013011523A1 publication Critical patent/WO2013011523A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F04B39/0094—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 crankshaft
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric

Definitions

  • the present disclosure generally relates to compressors, and, more particularly, relates to a compressor capable of producing an energy efficient compression effect.
  • Compressors are devices or machines that are employed to increase pressure of a compressible fluid.
  • the term 'compressible fluid' as mentioned herein may refer to any compressible fluid, either gas or vapour.
  • the inlet pressure of the compressible fluid may be of any value from a deep vacuum to a high positive pressure.
  • the discharge pressure i.e. the pressure to which the compressible fluid is required to be raised, may range from sub atmospheric levels to high values in tens of thousands of pounds per square inch.
  • the compressors may be of 2 broad types, positive displacement compressors and centrifugal compressors.
  • the positive displacement type compressors are either reciprocating type compressors or rotary type compressors. These compressors work on the principle of compressing a volume of the compressible fluid to produce the desired pressure change.
  • the centrifugal type compressors work on the principle of increasing velocity of the compressible fluid to produce the desired pressure change.
  • compressors are innumerable.
  • the compressors may be used as pumps for fluid transport. Further, the compressors may also be employed in pneumatic applications.
  • the most common use of the compressors may be in refrigeration and cooling equipments, such as room Air Conditioners (ACs), car ACs, refrigerators and refrigeration and cooling plants.
  • ACs room Air Conditioners
  • cars ACs car ACs
  • refrigerators refrigeration and cooling plants.
  • Cold storages and artificially conditioned environments are always in huge demand.
  • any energy input into the system that is being maintained at a set temperature requires a corresponding increase in the energy removal rate.
  • the increase in the energy removal rate requires an increase in energy consumption. Accordingly, reducing the overall energy consumed by these equipments is highly desirable, especially considering the present day scenario where the energy supplies globally are dwindling.
  • An object of the present disclosure is to provide a compressor, which is capable of producing an energy efficient compression effect.
  • Another object of the present disclosure is to provide a compressor that consumes very less energy, thereby making such a compressor a green solution towards energy problems.
  • a yet another object of the present disclosure is to provide a compressor that is equally effective in addressing the needs of cooling and refrigerating equipments.
  • a yet another object of the present disclosure is to provide a compressor that is compact and light weight, thereby solving the problems of shortage of storage spaces.
  • a yet another object of the present disclosure is to provide a compressor that may be effectively employed in a cooling system.
  • the present disclosure provides a compressor capable of producing an energy efficient compression effect.
  • the compressor includes a driving unit having a driven shaft.
  • the driving unit is capable of being connected to an external power source for driving the driven shaft.
  • the compressor includes a transmission unit comprising a gear assembly abuttingly coupled to the driven shaft.
  • the compressor includes an operating unit coupled to the gear assembly.
  • the gear assembly controllably transfers motion of the driven shaft to the operating unit, wherein the operating unit produces the energy efficient compression effect by compressing an operating medium.
  • the present disclosure provides a compressor capable of producing an energy efficient compression effect.
  • the compressor includes a driving unit having a driven shaft.
  • the driving unit is capable of being connected to an external power source for driving the driven shaft.
  • the compressor includes a transmission unit including a gear assembly abuttingly coupled to the driven shaft.
  • the compressor also includes an operating unit.
  • the operating unit includes an operating shaft operatively coupled to the gear assembly of the transmission unit.
  • the operating unit includes an operating section operatively coupled to the operating shaft.
  • the operating section is capable of producing the energy efficient compression effect by compressing an operating medium.
  • the compressor is characterized in that the transmission unit controllably transfers a motion of the driven shaft to the operating shaft.
  • the compressor is characterized in that the operating shaft transfers the controlled motion to the operating section.
  • the compressor is characterized in that the operating shaft and the driving unit are structurally configured opposite to each other such that an axis of the operating shaft is parallel to an axis of the driven shaft.
  • the present disclosure provides a valve plate for a compressor capable of producing energy efficient compression effect.
  • the compressor includes a plurality of compression cylinders.
  • the valve plate includes a seating capable of being rested over end portions of the plurality of compression cylinders.
  • the seating includes a suction side surface and a discharge side surface.
  • the seating includes a plurality of suction holes disposed on the. suction side surface of the seating.
  • the plurality of suction holes is capable of allowing an operating medium to flow into the each of the plural ity of compression cylinders.
  • the seating includes a plurality of discharge holes disposed on the discharge side surface of the seating.
  • the plurality of discharge holes is capable of allowing a compressed operating medium to exit the each of the plurality of compression cylinders.
  • the valve plate is characterized in that a bore size of the plurality of suction holes is about equivalent to a bore size of the plurality of discharge holes.
  • the present disclosure provides a compressor capable of producing an energy efficient compression effect.
  • the compressor includes a driving unit having a driven shaft.
  • the driving unit is capable of being connected to an external power source for driving the driven shaft.
  • the compressor includes an operating unit including an operating shaft operatively coupled to the driven shaft, and an operating section operatively coupled to the operating shaft.
  • the operating section includes a plurality of compression cylinders.
  • the operating section includes at least one valve plate including a seating capable of being rested over end portions of the plural ity of compression cylinders.
  • the seating includes a suction side surface and a discharge side surface. Further, the seating includes a plurality of suction holes disposed on the suction side surface of the seating.
  • the plurality of suction holes is capable of allowing an operating medium to flow into the plurality of compression cylinders.
  • the seating includes a plurality of discharge holes disposed on the discharge side surface of the seating.
  • the plurality of discharge holes is capable of allowing the compressed operating medium to exit the plurality of compression cylinders.
  • the valve plate is characterized in that a bore size of the plurality of suction holes is about equivalent to a bore size of the plurality of discharge holes.
  • the present disclosure provides a cooling system that includes a compressor capable of producing an energy efficient compression effect, and a heat transfer circuit capable of uti lizing the compressed operating medium for producing the air conditioning effect.
  • the compressor includes a driving unit having a driven shaft.
  • the driving unit capable of being connected to an external power source for driving the driven shaft.
  • the compressor includes a transmission unit comprising a gear assembly abuttingly coupled to the driven shaft, and an operating unit.
  • the operating unit includes an operating shaft operatively coupled to the gear assembly, and an operating section operatively coupled to the operating shaft.
  • the operating section is capable of producing a compression effect by compressing an operating medium
  • the compressor is characterized in that, the transmission unit controllably transfers motion of the driven shaft to the operating shaft, and the operating shaft transfers the controlled motion to the operating section to produce the energy efficient compression effect.
  • the operating shaft and the driving unit are structurally configured opposite to each other such that an axis of the operating shaft is parallel to an axis of the driven shaft.
  • the cooling system further includes a heat transfer circuit coupled to the compressor, the heat transfer circuit capable of utilizing the compressed operating medium for producing the air conditioning effect.
  • FIG. 1 is an overview of a compressor, according to an embodiment of the present disclosure
  • FIG. 2 is a perspective view of the compressor of FIG. 1 , according to an embodiment of the present disclosure
  • FIG. 3 is a perspective view of the compressor of FIG. 1 being driven by a belt and pulley system, according to an embodiment of the present disclosure
  • FIG. 4 is a disassembled view of the compressor of FIG. 1 , according to an embodiment of the present disclosure
  • FIG. 5A and 5B are perspective views of a gear assembly, according to various embodiments of the present disclosure.
  • FIG. 6 is a perspective view of a discharge side of a valve plate, according to an embodiment of the present disclosure.
  • FIG. 7 is a disassembled view of the discharge side of the valve plate (of FIG. 6), according to an embodiment of the present disclosure
  • FIG. 8 is a perspective view of a suction side of a valve plate, according to an embodiment of the present disclosure.
  • FIG. 9 is a disassembled view of the suction side of the valve plate (of FIG. 8), according to an embodiment of the present disclosure.
  • FIG. 10 is a perspective view of a head plate, according to an embodiment of the present disclosure.
  • FIG. 1 1 is a perspective view of a head plate, according to another embodiment of the present disclosure.
  • FIG. 12 is a block diagram of a cooling system, according to an embodiment of the present disclosure.
  • a compressor 1 000 includes a driving unit 100, a transmission unit 500 operatively coupled to the driving unit 100 and an operating unit 700 operatively coupled to the transmission unit 500.
  • the driving unit 100 may include a driven shaft 10.
  • the driving unit 100 may be capable of being connected to an external power source (not shown) for driving the driven shaft 10.
  • the driving unit 100 may include a motor comprising a stator-rotor assembly 20.
  • the stator-rotor assembly 20 may include a stator 22, and a rotor 24 operatively coupled to the stator 22.
  • the stator 22 may be capable of being connected to the external power supply, which in this case is an electrical power source, for driving the rotor 24. It should be apparent to a person skilled in the art that the stator 22, when connected to the electrical power source, may act as a field magnet. This conversion of the stator 22 into a field magnet may drive the rotor 24.
  • the rotor 24 may include a rotor shaft 1 7 in operational communication with the rotor 24.
  • the rotor shaft 17 may further be operably coupled to the driven shaft 10. Accordingly, the rotation of the rotor 24 may rotate the rotor shaft 17, which in turn may drive the driven shaft 10.
  • the driving unit 100 may be a belt and pulley system 200 (as shown in FIG. 3).
  • Such belt and pulley system 200 may be similar to those existing in automobile engines for supplying driving means to compressors installed for conditioning cabin air of automobiles.
  • the belt and pulley system 200 may be in operational communication with the driven shaft 10 for driving the driven shaft 10.
  • the external power source may be an automobile engine from which the belt over the pulley system 200 drives the power to drive the driven shaft 10.
  • the driven shaft 10 may include a first end portion 1 1 and a free end portion 12 distal to the first end portion 1 1.
  • the first end portion 1 1 is operably coupled to the driving unit 100.
  • the first end portion 1 1 is operably coupled to the rotor shaft 17.
  • the first end portion 1 1 is operably coupled to the belt over a pulley system 200.
  • the free end portion 12 may include a plurality of teeth 14 configured thereon as depicted in FIGS. 2-5.
  • the plurality of teeth 14 configures a gear on the free end portion 12 of the driven shaft 10.
  • the driven shaft 10 may be composed of metallic materials, or alloys, or any other material which makes it suitable for operation.
  • the driven shaft 1 0 may include about 10 to about 15 teeth.
  • the driven shaft 10 may include about 13 teeth in number.
  • the transmission unit 500 is provided to regulate the motion of the driven shaft 10. This regulation of the motion of the driven shaft 10 allows the driven shaft 10 to be operated by a low rating external power source, thereby reducing the overall energy consumption of the compressor 1000.
  • the transmission unit 500 will now be described in detail.
  • the transmission unit 500 includes a gear assembly 410 abuttingly coupled to the driven shaft 10.
  • the transmission unit 500 regulates the motion of the driven shaft 10 via this gear assembly 410.
  • the gear assembly 410 may include a master gear 420 in operational communication with the free end portion 12 of the driven shaft 10. More specifically, the gear assembly 410 may include the master gear 420 operatively coupled to the plurality of teeth 14 configured at the free end portion 12 of the driven shaft 10. The operable coupling between the master gear 420 and the free end portion 12 of the driven shaft 10 allows a controlled transmission of the motion of the driven shaft 10 to the gear assem b ly 410.
  • the gear assembly 4 1 0 may include a plurality of transmission gears 430 (only one transmission gear 430 is shown in FIG. 5 A and 2 transmission gears 430 are shown in FIG. 5B) arranged between the free end portion 12 of the driven shaft 10 and the master gear 420. More specifically, the free end portion 12 of the driven shaft 10 may be abuttingly coupled to at least one of the transmission gears 430. Even more specifically, the plurality of teeth 14 on the free end portion 12 may be abuttingly coupled to the at least one of the transmission gears 430. Further, at least one of the transmission gears 430 may be abuttingly coupled to the master gear 420. The operational communication between the free end portion 12 of the driven shaft 10, transmission gears 430 and the master gear 420 allows a controlled transmission of the motion of the driven shaft 10 to the gear assembly 410.
  • the gear assembly 410 may include any number of gears.
  • the gear assembly 410 may include 14 gears (12 transmission gears and one master gear).
  • the gear assembly 410 may include 7 gears (5 transmission gears and one master gear).
  • the gear assembly 410 may include 4 gears (2 transmission gears and one master gear).
  • the construction of the transmission gears 430 and the master gear 420 may vary based on sizing of the compressor 1000.
  • the master gear 420 may include about 80 teeth to about 90 teeth, and may have an outer diameter of about 75 millimetres (mm) to about 90 millimetres (mm), and a bore size of about 25 millimetres to about 40 millimetres.
  • the master gear 420 and the transmission gears 430 may be composed of metallic materials, or alloys, or any other suitable materials.
  • the operating unit 700 is coupled to the transmission unit 500.
  • the operating unit 700 is the operational hub of the compressor 1000. In other words, it is that part of the compressor 1000 where the compression of an operating medium (compressible fluid) may occur.
  • an operating medium compressible fluid
  • the term "operating medium” as mentioned herein may include a gas or a vapour.
  • the operating unit 700 may include an operating shaft 610, and an operating section 620 operatively coupled to the operating shaft 610.
  • the operating shaft 610 may be a crankshaft 610 (refer FIG. 4).
  • the crankshaft 610 may have a diameter in range of 25 millimetres and 50 millimetres, and a cut size of 3 millimetres and 5 millimetres.
  • the operating shaft 610 includes an operating end portion 612 and an engaged end portion 614.
  • the operating end portion 612 may be operatively coupled to the gear assembly 410 of the transmission unit 500.
  • the operating end portion 612 may be provided with a plurality of keys for allowing easy operative coupling with the gear assembly 410, which may include corresponding plurality of keys.
  • the engaged end portion 614 may be operatively coupled to the operating section 620.
  • the master gear 420 of the gear assembly 410 may be snugly fitted over the operating end portion 612 of the operating shaft 610 (as shown in FIGS. 2, 3 and 4). Such operational coupling allows the gear assembly 410 to transfer the controlled motion to the operating section 620 of the compressor 1000 via the operating shaft 610.
  • the operating shaft 610 may be operatively coupled to the gear assembly 410. More specifically, an operating end 612 of the operating shaft 610 may be operatively coupled to the master gear 420, which may be snugly fitted thereon for providing the operative coupling.
  • the operative shaft 610 in such configuration may be arranged such that an axis 'A' of the operating shaft 610 is paral lel to an axis ' X' of the driven shaft 10, and the operating shaft 610 and the driving unit 100 are structurally arranged opposite to each other.
  • Such arrangement of the operating shaft 610 and the driving unit 100 adds to the overall compactness of the compressor 1000.
  • Such compactness is very important to reduce the overall size of the compressor 1000 making it easily installable in installation locations that are suffering from shortage of storage spaces.
  • such configuration of the operating shaft 610 with respect to the driving unit 100 should not be construed as a limitation to the present disclosure.
  • the operating section 620 forms the core of the compressor 1000, and provides the compression effect in the compressor 1000. More specifically, the operating section 620 compresses an operating medium in the compressor 1 000.
  • the operating medium refers to a refrigerant that is required to be compressed in the compressor 1000. Suitable examples of such refrigerants may include, but are not limited to, R-401A, R-404A, R-408A, and the like. In one embodiment, the operating medium may be air.
  • the operating section 620 may be similar to the operating sections existing in the reciprocating type compressors. According to this embodiment, the operating section 620 may therefore include a plurality of compression cylinders 800 (2 compression cylinders shown in FIGS. 1 and 4). Further, it should be noted that the terms 'plurality of compressions cylinders 800' and 'plurality of cylinders 800' may interchangeably used in the present disclosure.
  • Each of the plurality of compression cylinders 800 may be similar in construction. Each of the plurality of compression cylinders 800 may be fitted with a piston member 810. The piston member 810 may be capable of reciprocating inside the each of the plurality of compression cylinders 800.
  • the piston member 810 may be operatively coupled to the operating shaft 610.
  • the piston member 810 may be operatively coupled to a crankpin 615 of the operating shaft 610 (as shown in FIGS. 1 and 4).
  • the operational coupling of the operating shaft 610 and the piston member 810 of the each of the plurality of compression cylinders 800 allows the piston member 810 to receive driving force transferred via the operating shaft 61 0. This enables the piston member 810 to reciprocate inside the each of the plurality of cylinders 800.
  • each of the plurality of compression cylinders 800 may be composed of metallic materials, alloys, or other similar materials suitable.
  • the operating section 620 may include at least one valve plate 625 fitted on a top end portion 630 of the each of the plurality of cylinders 800.
  • the at least one valve plate 625 may regulate the suction and discharge of the operating medium acted upon in the each of the plurality of compression cylinders 800.
  • the at least. one valve plate 625 will now be described with reference to FIGS. 6- 7.
  • FIG. 6 shows a perspective view of a discharge side of the valve plate 625, according to an embodiment of the present disclosure.
  • FIG. 7 is a disassembled view of the discharge side of the valve plate 625.
  • FIG. 8 is a perspective view of a suction side of the valve plate 625, according to an embodiment of the present disclosure.
  • FIG. 9 is a disassembled view of the suction side of the valve plate 625, according to an embodiment of the present disclosure.
  • the valve plate 625 includes a seating 626.
  • the seating 626 may be capable of being rested over the top end portions 630 of the plurality of compression cylinders 800.
  • the seating 626 is similar to seating that exists in valve plates known in the art.
  • the seating 626 includes a discharge side surface 632 and a suction side surface 634.
  • the discharge side surface 632 includes a plurality of discharge holes 627 disposed on the discharge side surface 632 of the seating 626.
  • the plurality of discharge holes 627 is capable of allowing the compressed operating medium (not shown) to exit from the each of the plurality of compression cylinders 800 during operation of the each of the plurality of cylinders 800.
  • the compressed operating medium refers to an operating medium in a compressed state, i.e., the operating medium which has been compressed by the action of the piston member 810 of the each of the plurality of cyl inders 800.
  • the seating 626 includes a plural ity of suction holes
  • the plurality of discharge holes 629 is capable of allowing an operating medium to enter the each of the plurality of compression cylinders 800.
  • valve plate 625 is characterized in that a bore size of the plurality of discharge holes 627 is about equivalent to a bore size of the plurality of suction holes 629.
  • valve plate 625 is characterized in that a bore size of the plurality of discharge holes 627 is about similar to a bore size of the plurality of suction holes 629. [00070] In yet another embodiment, the bore size of the plurality of discharge holes 627 and the plurality of suction holes 629 may be between about 5 millimetres to about 15 millimetres.
  • the valve plate 625 may further include a discharge side reed valve 636 attached to the discharge side surface 632 of the seating 626. More specifically, the discharge side reed valve 636 is bolted into holes 641 on the discharge side surface 632 for attaching the discharge side reed valve 636 on the discharge side surface 632. The bolting may be done using one or more bolts 640.
  • the discharge side reed valve 636 is capable of operating for allowing the operating medium to flow into the each of the plurality of compression cylinders 800. More specifically, the discharge side reed valve 636 may be capable of opening for allowing the compressed operating medium to flow out of the each of the plurality of compression cylinders 800. The operation of the discharge side reed valve 636 is based on pressure variation inside the each of the plurality of compression cylinders 800 created due to the movement of the piston member 810 therein.
  • the valve plate 625 may further include a suction side reed valve 638 attached to the suction side surface 634 of the seating 626. More specifically, the suction side reed valve 638 is pinned into the suction side surface 634 using pins 643 that attach the suction side reed valve 638 on the suction side surface 634. .
  • the suction side reed valve 638 is capable of operating for allowing the operating medium to flow into the each of the plurality of compression cylinders 800. More specifically, the suction side reed valve 638 may be capable of opening for allowing the operating medium to flow into the each of the plurality of compression cylinders 800. The operation of the suction side reed valve 638 is based on pressure variation inside the each of the plurality of compression cylinders 800 caused due to the movement of the piston member 810 therein. More specifically, the suction side reed valve 638 may open when a positive pressure exists in the each of the plurality of compression cylinders 800. [00075] Furthermore, the operating section 620 may include at least one head plate 650 (hereinafter referred to as head plate 650). The head plate 650 will now be described with reference to FIGS. 10- 1 1 .
  • the head plate 650 may be designed to be disposed over the plurality of cylinders 800. More specifically, the head plate 650 may be placed over the discharge side surface 632 of the valve plate 625. The head plate 650 facilitates an entry and exit of the operating medium in the each of the plurality of cylinders 800. More specifically, during operation of the plurality of cylinders 800, the head plate 650 allows an accumulation and discharge of the operating medium over the plurality of cylinders 800.
  • the head plate 650 may include a bulge 652 extending outwardly from the plurality of cylinders 800. The bulge 652 may be capable of encapsulating the plurality of cylinders 800.
  • the head plate 650 has a depth of about 15 millimetres to about 30 millimetres, and has a length of about 100 millimetres to about 140 millimetres.
  • these dimensions of the head plate 650 are provided for exemplary purposes only and should not be construed as a limitation to the present disclosure.
  • the head plate 650 includes a suction inlet 656 capable of allowing the operating medium to flow into the head plate 650.
  • the suction inlet 656 allows the operating medium to flow into the head plate 650 from a reservoir (not shown) capable of storing the operating medium therein.
  • the head plate 650 includes a discharge outlet 654. The discharge outlet 654 allows the compressed operating medium to flow back into the reservoir.
  • the head plate 650 may further include a division wall 658.
  • the division wall 658 is designed to divide the head plate 650 into two zones, such as Discharge zone (D) and Suction zone (S). Such division also precludes any intervention of the operating medium and the compressed operating medium during operation of the plurality of cylinders 800.
  • the head plate 650 may be placed over the valve plate 625 such that the discharge holes 627 lie in the Discharge zone (D), and the suction holes 629 lie in the Suction zone (S).
  • FIG. 1 1 shows the discharge plate 650 according to another embodiment of the present disclosure. As shown in the FIG.
  • the discharge plate 650 includes a division wall 670 to divide the head plate into a Discharge zone D' and a Suction zone S' . Such division also precludes any intervention of the operating medium and the compressed operating medium during operation of the plurality of cylinders 800.
  • the head plate 650 may be placed over the valve plate 625 such that the discharge holes 627 lie in the Discharge zone (D), and the suction holes 629 lie in the Suction zone (S). It will be clear from FIG. 1 1 that in such embodiment the wall 670 cuts through the suction side 'S' and the discharge side 'D' as compared to merely dividing the head plate 650 into a suction side 'S' and a discharge side 'D', as is the case in FIG. 10.
  • the operating section 620 may include a central spinning rotor (not shown in the figures) having a plurality of vanes attached thereto.
  • the central spinning rotor may be operatively coupled to the operating shaft 610 of the operating unit 700 for transferring the controlled motion of the driven shaft 10 to the central spinning rotor, thereby producing the energy efficient compression effect.
  • the operating section 620 is similar to operating sections existing in the rotary type compressors. Accordingly, the operating medium may be acted upon by the central spinning rotor to increase a pressure thereof. More specifically, the operating section 620 according to this embodiment may allow the operating medium to get into operation with the central spinning rotor, which using its plurality of vanes may act on the operating medium to increase a pressure of the operating medium.
  • the operating section 620 may include operating sections existing in compressors known in the art.
  • the operating section 620 may be similar to the operating section of a centrifugal type compressor, or other rotary type compressors, such as rotary screw type compressors, and the like.
  • the compressor 1000 may include a pump assembly (not shown).
  • the pump assembly may include a small pneumatic pump (not shown) capable of supplying pre-determined quantities of lubricant to the piston members, such as the piston member 810, the operating shaft 610 and the driven shaft 10.
  • the pneumatic pump keeps the piston members well lubricated during operation of the compressor 1000.
  • the compressor 1000 may additionally include a support stand 860 capable of supporting various components of the compressor 1000.
  • the support stand 860 may be composed of sturdy materials capable of supporting the vigour during the operation of the compressor 1000.
  • the support stand 860 may preferably be composed of metallic materials, such as steel.
  • the compressor 1000 may be hermetically sealed in a casing.
  • the hermetically sealing may be done similar to the sealing methods known in the art.
  • the casing may be similar to the casing known in the art.
  • Such sealing insulates the compressor 1000 from the outer environment.
  • the compressor 1000 may be oil filled.
  • the compressor 1000 is required to be connected to an external power supply. More specifically, the driving unit 100 of the compressor 1000 may be required to be operatively coupled to the external power supply.
  • the external power supply may be an electrical power supply available in households or industrial establishments. In case the compressor is required to be part of a car air conditioning system, the external power supply may be an automobile engine.
  • the operational coupling of the driving unit 100 to the external power supply enables the driving unit 100 to rotate the driven shaft 10.
  • the rotation of the driven shaft 10 accordingly transfers the motion thereof to the transmission unit 500, and more particularly, the gear assembly 4 1 0 of the transm ission unit 500.
  • the teeth 14 (gear) configured at the free end portion 12 of the driven shaft 10 may facilitate the transfer of the motion of the driven shaft 10 to the master gear 420 to which it is operatively coupled. This may lead to rotation of the master gear 420.
  • the rotation of the master gear 420 controllably transfers the motion of the driven shaft 10 to the operating shaft 610.
  • the rotation of the operating shaft 610 activates the operating section 620.
  • the operating section 620 may act on the operating medium, which may be sucked into the operating section 620 via the head plate 650.
  • the sucked operating medium may become accumulated in the head plate 650. Thereafter, the motion of the piston member 8 1 0 in the each of the plurality of cylinders 800 may allow the operating medium to be introduced in the each of the plurality of cylinders 800 via the at least one valve plate 625.
  • the moving piston member 810 may then act upon and compresses the operating medium to a desired pressure, thereby providing the energy efficient compression effect.
  • Such compressed operating medium may thereafter be taken out of the plurality of cylinders 800.
  • the compressed operating medium may thereafter be used in a refrigeration system or an air-conditioning system as the case may be.
  • the pump assembly may keep the piston member 810 and the operating shaft 610 well lubricated.
  • the present disclosure provides a cooling system 2000 for providing energy efficient cooling.
  • the cooling system 2000 is shown with reference to FIG. 12.
  • the cooling system 2000 includes a compressor, such as compressor 1000, and a heat transfer circuit 1 100 operatively coupled to the compressor.
  • the compressor includes a driving unit having a driven shaft.
  • the driving unit is capable of being connected to an external power source for driving the driven shaft.
  • the compressor includes a transmission unit that includes a gear assembly abuttingly coupled to the driven shaft.
  • the compressor includes an operating unit.
  • the operating unit includes an operating shaft operatively coupled to the gear assembly of the transmission unit, and an operating section operatively coupled to the operating shaft.
  • the operating section is capable of producing the energy efficient compression effect by compressing an operating medium.
  • the compressor is characterized in that the transmission unit controllably transfers a motion of the driven shaft to the operating shaft. Further, the compressor is characterized in that the operating shaft transfers the controlled motion of the driven shaft to the operating section of the operating unit.
  • the compressor is characterized in that the operating shaft and the driving unit are structurally configured opposite to each other such that an axis of the operating shaft is parallel to an axis of the driven shaft.
  • the heat transfer circuit may be an air conditioning circuit capable of providing energy efficient air conditioning.
  • the air conditioning circuit is similar to the air conditioning circuit known in the art. It will be apparent to a person skilled in the art that such a circuit usually includes a cooling coil and a heating coil in operational communication with the compressor 1000. Further, the air conditioning circuit may additionally include an air circulation sub circuitry including a fan and blower.
  • the heat transfer circuit may include a refrigeration circuit.
  • the refrigeration circuit is similar to the refrigeration circuits employed in conventional refrigeration systems.
  • the heat transfer circuit may include a chilling circuit.
  • the chilling circuit is similar to the chilling circuits employed in conventional chilling systems.
  • the present disclosure provides a compressor capable of producing an energy efficient compression effect.
  • the compressor includes a driving unit having a driven shaft.
  • the driving unit is capable of being connected to an external power source for driving the driven shaft.
  • the compressor includes an operating unit.
  • the operating unit includes an operating shaft operatively coupled to the driven shaft, and an operating section operatively coupled to the operating shaft.
  • the operating section includes a plurality of compression cylinders, and at least one valve plate.
  • the at least one valve plate includes a seating capable of being rested over a top end portion of each of the plurality of compression cylinders.
  • the seating includes a suction side surface and a discharge side surface, a plurality of suction holes disposed on the suction side surface of the seating.
  • the plurality of suction holes are capable of allowing an operating medium to flow into the each of the plurality of compression cylinders.
  • the seating includes a plurality of discharge holes disposed on the discharge side surface of the seating.
  • the plurality of discharge holes are capable of allowing a compressed operating medium to exit the each of the plurality of compression cylinders.
  • the valve plate is characterized in that a bore size of the plurality of suction holes is about equivalent to a bore size of the plurality of discharge holes.
  • the Novel Compressor shows lowest Free Ampere reading of about 0.5 Ampere, and Load Ampere reading of about 1.3 Ampere among the comparative compressors, while producing almost the same pressures. This clearly highlights the energy efficiency of the Novel Compressor, which is attributed to its unique design. Further, the Novel Compressor was able to perform the same when integrated with a cooling system, which in this case is a standard 1.5 Tonne Air conditioning system.
  • the Novel Compressor gave excellent performance in high ambient temperatures ranges, in which the standard compressors either tripped or showed considerable reduction in performance.
  • the Novel Compressor was able to produce cooling when applied in the cooling system with the outside ambient temperatures in range of about 50 degrees Celsius to about 55 degree Celsius.
  • the compressor 1000 is capable of producing an energy efficient compression effect.
  • the energy efficient compression effect is due to the introduction of a transmission unit, such as transmission unit 500, which allows use of a low rating driving unit 100 in the compressor. This makes the compressor 1000 a green solution towards addressing the ever burgeoning cooling requirements.
  • the compressor 1000 consumes very less energy and is equally effective in addressing the cooling and refrigerating needs of cooling and refrigeration equipments. This is attributed to the to the transmission unit 500 and employing the valve plate 625 and the head plate 650 in the present disclosure.
  • the compressor 1 000 is compact despite adding the transmission unit 500. This compactness is mainly because the "driving unit 100 is structurally configured opposite to the transmission unit 500 as described above. This saves valuable installation spaces in households and industrial spaces.
  • the compressor 1000 is sturdy and highly durable during operation, thereby adding to its reliability. This is due to the use of highly robust and durably material for the construction of the compressor 1000.
  • the compressor 1000 is capable of being installed into an automobile. Therefore, the compressor 1000 may be capable of driving an air conditioner of an automobile.
  • the compressor 1000 is of high performance, and may be able to provide sustained performance in high ambient temperatures.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un compresseur (1000) apte à produire un effet de compression écoénergétique. Le compresseur (1000) comprend une unité d'entraînement (100) ayant un arbre entraîné, une unité de transmission (500) qui comprend un ensemble d'engrenage (410) accouplé en butée à l'arbre entraîné (10), et une unité de commande (700) ayant un arbre de commande (610) couplé fonctionnellement à l'ensemble d'engrenage (410), et une section travaillante (620). L'unité d'entraînement (100) peut être reliée à une source d'énergie extérieure pour entraîner l'arbre entraîné (10). La section travaillante (620) peut produire l'effet de compression avec un bon rendement énergétique en comprimant un milieu de travail. L'unité de transmission (500) transmet de façon commandée un mouvement de l'arbre entraîné (10) à l'arbre de commande (610), lequel transmet à son tour le mouvement commandé de l'arbre entraîné (10) à la section de commande (620) de l'unité de commande pour produire l'effet de compression écoénergétique.
PCT/IN2012/000495 2011-07-20 2012-07-13 Compresseur destiné à produire une compression écoénergétique Ceased WO2013011523A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IN2044DE2011 2011-07-20
IN2044/DEL/2011 2011-07-20

Publications (1)

Publication Number Publication Date
WO2013011523A1 true WO2013011523A1 (fr) 2013-01-24

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2151276Y (zh) * 1993-03-08 1993-12-29 山西机械电子信息开发公司 微型空气压缩机
US6315534B1 (en) * 1998-03-30 2001-11-13 Wen San Chou Air compressor having easily assembled structure
US20040105766A1 (en) * 2002-01-25 2004-06-03 Chou Wen San Air compressor having stable configuration
WO2004101993A1 (fr) * 2003-05-14 2004-11-25 Yoosung Enterprise Co., Ltd. Compresseur d'air
CN2697346Y (zh) * 2004-02-23 2005-05-04 王伟吉 可高压起动的打气泵
CN101349268A (zh) * 2005-06-09 2009-01-21 株式会社日立产机系统 螺旋压缩机
CN201671789U (zh) * 2010-04-30 2010-12-15 宁波布拉沃冲气具制造有限公司 电动气泵的活塞驱动结构
CN101915228A (zh) * 2010-06-30 2010-12-15 程志平 高压鼓风机

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2151276Y (zh) * 1993-03-08 1993-12-29 山西机械电子信息开发公司 微型空气压缩机
US6315534B1 (en) * 1998-03-30 2001-11-13 Wen San Chou Air compressor having easily assembled structure
US20040105766A1 (en) * 2002-01-25 2004-06-03 Chou Wen San Air compressor having stable configuration
WO2004101993A1 (fr) * 2003-05-14 2004-11-25 Yoosung Enterprise Co., Ltd. Compresseur d'air
CN2697346Y (zh) * 2004-02-23 2005-05-04 王伟吉 可高压起动的打气泵
CN101349268A (zh) * 2005-06-09 2009-01-21 株式会社日立产机系统 螺旋压缩机
CN201671789U (zh) * 2010-04-30 2010-12-15 宁波布拉沃冲气具制造有限公司 电动气泵的活塞驱动结构
CN101915228A (zh) * 2010-06-30 2010-12-15 程志平 高压鼓风机

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