EP1541868A1 - Refrigerant compressor - Google Patents
Refrigerant compressor Download PDFInfo
- Publication number
- EP1541868A1 EP1541868A1 EP04732026A EP04732026A EP1541868A1 EP 1541868 A1 EP1541868 A1 EP 1541868A1 EP 04732026 A EP04732026 A EP 04732026A EP 04732026 A EP04732026 A EP 04732026A EP 1541868 A1 EP1541868 A1 EP 1541868A1
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- EP
- European Patent Office
- Prior art keywords
- suction
- valve
- cylinder
- valves
- pressure
- 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.)
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Classifications
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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
- F04B39/0005—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 adaptations of pistons
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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
- F04B39/0027—Pulsation and noise damping means
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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
- F04B39/0027—Pulsation and noise damping means
- F04B39/0088—Pulsation and noise damping means using mechanical tuned resonators
-
- 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
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1066—Valve plates
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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
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
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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
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/12—Kind or type gaseous, i.e. compressible
Definitions
- the present invention relates to an improvement in efficiency of a hermetic compressor used in freezer-refrigerators, and the like.
- a hermetic compressor used in freezer-refrigerators, and the like has been strongly demanded.
- the suction efficiency is increased by, for example, providing a valve device of a compression part with two holes, and the compression efficiency is improved.
- Such a compressor is disclosed in, for example, Japanese Patent Unexamined Publication No. H3-175174.
- an example of a conventional hermetic compressor is described with reference to drawings.
- FIG. 6 is a sectional view showing a conventional refrigerant compressor
- FIG. 7 is an exploded perspective view showing a valve of a conventional refrigerant compressor.
- an outlet port 52A that is one end of a suction tube 52 is connected.
- Another end of the suction tube 52 is connected to a piping at the low-pressure side of a refrigerating cycle (not shown).
- a motor 53 includes a stator 54 and a rotor 55, so as to drive a compression part 56.
- refrigerating machine oil 57 is preserved in a bottom portion of the hermetic container 51.
- a coil spring 58 elastically supports the motor 53 and the compression part 56.
- the compression part 56 includes a cylinder head 61, a cylinder block 62, a valve plate 64, a suction reed valve 67, a piston 68, a connecting rod 70 and a suction muffler 30.
- the cylinder head 61 forms a suction space 61A and a discharge space 61B.
- the cylinder block 62 contains a cylinder 63.
- the valve plate 64 has two suction holes 65 and two discharge holes 66.
- the suction reed valve (hereinafter, referred to as "valve") 67 has a deformation part 67A.
- the connecting rod 70 is linked to an eccentric part 69A of a crank shaft 69.
- the suction muffler 30 communicates to a suction space 61A via a communicating tube 30A and to the suction hole 65 of the valve plate 64, and sucks a refrigerant gas from an inlet port 30B.
- the motor 53 drives the compression part 56, so that the piston 68 reciprocates in the cylinder 63.
- a low temperature and low pressure refrigerant gas returning from an external refrigerating cycle (not shown) is firstly sucked into the hermetic container 51 from the suction tube 52.
- the refrigerant gas is further sucked from the inlet port 30B of the suction muffler 30 and passes through the suction hole 65 via the communicating tube 30A.
- the suction stroke by flexing the deformation part 67A of the valve 67, the refrigerant gas opens the valve 67 and is led to the cylinder 63.
- the valve 67 is closed.
- the refrigerant gas is compressed to high temperature and high pressure, passes from the discharge hole 66 through a discharge tube (not shown) and is led to the external refrigerating cycle (not shown) so as to be used for a refrigerating operation.
- the valve 67 is so designed as to have a natural frequency for carrying out an opening and closing operation with good timing in accordance with a low-speed operation frequency. Therefore, the compressor is capable of operation with a reduced suction loss and a high volumetric efficiency.
- valve 67 As a solution to reduce the backflow of a refrigerant gas due to delayed closing of the valve 67, designing the valve 67 to have a high natural frequency in accordance with the high-speed operation is considered. In this case, since the spring constant of the deformation part 67A is increased, an amount of flexure is reduced, so that the suction loss is increased and accordingly the refrigerating capacity and the refrigerating efficiency are lowered.
- the refrigerant compressor of the present invention includes a piston, a cylinder and a valve plate.
- the valve plate is provided at an opening end of the cylinder and includes a plurality of suction holes.
- the refrigerant compressor of the present invention further includes a plurality of suction reed valves, which is provided between the opening end of the cylinder and the valve plate, for opening and closing the plurality of suction holes, respectively.
- At least one of the suction reed valves has a natural frequency different from that of the other reed valves. With this configuration, even when an operation frequency is changed, delayed closing of the suction reed valve and reduction in an amount of flexure are prevented.
- FIG. 1 is a sectional view showing a refrigerant compressor in an embodiment of the preset invention.
- FIG. 2 is a front view showing a suction reed valve.
- FIG. 3 is a sectional view showing a cylinder head part.
- an outlet port 2A that is one end of a suction tube 2 is connected. Another end of the suction tube 2 is connected to a piping at the low-pressure side of a refrigerating cycle (not shown).
- a motor 3 includes a stator 4 and a rotor 5, and drives a compression part 6. Furthermore, refrigerating machine oil 7 is preserved in a bottom portion of the hermetic container 1.
- a coil spring 8 elastically supports the motor 3 and the compression part 6.
- the compression part 6 includes a cylinder head 101, a cylinder block 12, a valve plate 110, suction reed valves (hereinafter, referred to as "valve") 120A and 120B, a piston 18, a connecting rod 20 and a suction muffler 130.
- the cylinder head 101 forms a suction space 101A and a discharge space 101B.
- the cylinder block 12 contains a cylinder 13.
- the connecting rod 20 is linked to an eccentric part 19A of a crank shaft 19.
- the suction muffler 130 communicates to a suction space 101A via a communicating tube 130A and to suction holes 112A and 112B of the valve plate 110, and sucks a refrigerant gas from an inlet port 130B.
- the valve plate 110 has the suction holes 112A and 112B and discharge holes (not shown).
- the suction holes 112A and 112B are respectively inclined from opening portions 114A and 114B of the valve plate 110 at the side of the cylinder 13 to opening portions 114C and 114D of the valve plate 110 at the side of cylinder head 101 in the direction in which a distance between the suction holes is reduced.
- the valves 120A and 120B have deformation parts 122A and 122B having different lengths each other, respectively. Since the deformation part 122A is longer than the deformation part 122B, the spring constant of the valve 120A is smaller, and the valve 120A has a lower natural frequency than that of the valve 120B.
- valves 120A and 120B are asymmetric with respect to centerlines 124A and 124B of the deformation parts 122A and 122B. Positions of center points of the suction holes 112A and 112B correspond to points 126A and 126B of the valves 120A and 120B, respectively.
- Seal parts 128A and 128B seal the suction holes 112A and 112B provided on the valve plate 110.
- FIG. 4 is a graph showing a pressure in a cylinder and an amount of flexure of a reed valve in one stroke in a low-speed operation of a refrigerant compressor in an embodiment of the present invention.
- FIG. 5 is a graph showing a pressure in a cylinder and an amount of flexure of a reed valve in one stroke in a high-speed operation of a refrigerant compressor in an embodiment of the present invention.
- the motor 3 drives the compression part 6, so that the piston 18 reciprocates in the cylinder 13.
- a low temperature and low pressure refrigerant gas returning from an external refrigerating cycle (not shown) is firstly sucked into the hermetic container 1 from the suction tube 2.
- the refrigerant gas is further sucked from the inlet port 130B of the suction muffler 130 and passes through the suction holes 112A and 112B via the communicating tube 130A.
- the suction stroke by flexing the deformation parts 122A and 122B of the valves 120A and 120B, the refrigerant gas opens the valve 120A and 120B and is led to the cylinder 13.
- valves 120A and 120B are closed, and the refrigerant gas is compressed to high temperature and high pressure, passes from the discharge hole through a discharge tube (not shown) and is led to the external refrigerating cycle to be used for a refrigerating operation.
- the point 140A means a point at which the gas pressure load generated by differential pressure becomes larger than a resultant force of flexure load of the valves 120A-120B and an adhesion force with the viscosity of refrigerating machine oil at the seal parts of the valves 120A-120B.
- valves 120A and 120B are closed at a point 140B at which the pressure in the cylinder 13 exceeds the pressure in the suction space 101A of the cylinder head 101, and suction of the refrigerant gas from the suction muffler 130 is completed.
- the valve 120A repeats opening and closing operations 150A twice at a natural frequency in primary deformation mode while flexing the deformation part 122A. Since the valve 120A is selected to have a natural frequency corresponding to a low-speed operation frequency, the valve 120A completes closing substantially with the same timing as the point 140B. Furthermore, since the spring constant of the valve 120A is small, even under conditions that the flow rate of sucked gas is slow during a low-speed operation, a suction loss due to the shortage of an amount of flexure is not increased.
- the valve 120B has a natural frequency and a spring constant higher than those of the valve 120A, and repeats opening and closing operations 150B four times between the point 140A and the point 140B.
- the valve 120B opens widely with a certain amount of flexure according to the circulation amount of refrigerant at the first to third opening and closing operations 150B.
- the fourth opening and closing operation since in the compression stroke, the differential pressure between the pressure in the cylinder 13 and the pressure in the suction space 101A of the cylinder head 101 is extremely small. At this time, the refrigerant gas flows in the suction hole 112A of the valve 120A that flexes more largely.
- valve 120B hardly flexes and it completes opening and closing operation near the point 141B.
- the valve 120B repeats opening and closing operations 151B three times and flexes with a certain amount of flexure according to the circulation amount of refrigerant, and then completes closing with good timing.
- the point 141A means a point at which the pressure in the cylinder 13 becomes lower than the pressure in the suction space 101A of the cylinder head 101.
- the point 141B means a point at which the pressure in the cylinder 13 exceeds the pressure in the suction space 101A of the cylinder head 101.
- the valve 120A opens widely in a certain amount of flexure according to the circulation amount of refrigerant at the first opening and closing operation 151A.
- the second opening and closing operation since in a compression stroke, the differential pressure between the pressure in the cylinder 13 and the pressure in the suction space 101A of the cylinder head 101 is extremely small. Therefore, the refrigerant gas passes through the suction hole 112B of the valve 120B that flexes more largely. Consequently, the valve 120A hardly flexes and it completes the opening and closing operation near the point 141B.
- valves 120A and 120B are asymmetric with respect to the centerlines 124A and 124B of the deformation parts 122A and 122B. Therefore, working points 126A and 126B of the gas pressure load that act on the valves 120A and 120B deviate from centerlines 124A and 124B of the flexing deformation of the valves 120A and 120B. Thus, the valves 120A and 120B start to open with torsion deformation. That is to say, torsional moment due to gas pressure load acts on the valves 120A and 120B.
- both of the shapes of the valves 120A and 120B are asymmetric with respect to the centerlines 124A and 124B of the deformation parts 122A and 122B. However, they may be configured so that only one of the shapes is asymmetric.
- a refrigerant gas inside the hermetic container 1 passes through the suction space 101A in a high-temperature cylinder head 101 via the suction muffler 130 and is sucked into the cylinder 13 from the suction holes 112A and 112B provided on the valve plate 110.
- the refrigerant gas inside the cylinder 13 is in a high temperature state of about 100°C by a compression action and is discharged to a discharge space 101B of the cylinder head 101.
- the cylinder head 101 is heated to high temperature state of about 80°C.
- the suction space 101A in the cylinder head 101 can be configured to have a reduced volume and heat receiving area, so that the thermal transmission to the flowing refrigerant gas is reduced.
- both of the suction holes 112A and 112B are inclined, but only one of them may be inclined.
- the number of the valves 120A and 120B is two. However, when the number is three or more, the same effect can be obtained.
- the natural frequency is changed by varying the lengths of the valves 120A and 120B.
- the same effect can be obtained even when the natural frequency is changed by varying the widths or shapes of the valves 120A and 120B.
- a refrigerant compressor of the present invention includes a piston, a cylinder and a valve plate.
- the valve plate is provided at an opening end of the cylinder and has a plurality of suction holes.
- the refrigerant compressor of the present invention further includes a plurality of suction reed valves provided between the opening end of the cylinder and the valve plate, and opens and closes the plurality of suction holes, respectively. At least one of the suction reed valves has a natural frequency different from that of the other reed valves.
Abstract
Description
- The present invention relates to an improvement in efficiency of a hermetic compressor used in freezer-refrigerators, and the like.
- Recently, an improvement in efficiency of a hermetic compressor used in freezer-refrigerators, and the like, has been strongly demanded. In a conventional hermetic compressor, the suction efficiency is increased by, for example, providing a valve device of a compression part with two holes, and the compression efficiency is improved. Such a compressor is disclosed in, for example, Japanese Patent Unexamined Publication No. H3-175174. Hereinafter, an example of a conventional hermetic compressor is described with reference to drawings.
- FIG. 6 is a sectional view showing a conventional refrigerant compressor; and FIG. 7 is an exploded perspective view showing a valve of a conventional refrigerant compressor. To a
hermetic container 51, anoutlet port 52A that is one end of asuction tube 52 is connected. Another end of thesuction tube 52 is connected to a piping at the low-pressure side of a refrigerating cycle (not shown). Amotor 53 includes astator 54 and arotor 55, so as to drive acompression part 56. Furthermore, refrigeratingmachine oil 57 is preserved in a bottom portion of thehermetic container 51. Acoil spring 58 elastically supports themotor 53 and thecompression part 56. - The
compression part 56 includes acylinder head 61, acylinder block 62, avalve plate 64, asuction reed valve 67, apiston 68, a connectingrod 70 and asuction muffler 30. Thecylinder head 61 forms asuction space 61A and adischarge space 61B. Thecylinder block 62 contains acylinder 63. Thevalve plate 64 has twosuction holes 65 and twodischarge holes 66. The suction reed valve (hereinafter, referred to as "valve") 67 has adeformation part 67A. The connectingrod 70 is linked to aneccentric part 69A of acrank shaft 69. Thesuction muffler 30 communicates to asuction space 61A via a communicatingtube 30A and to thesuction hole 65 of thevalve plate 64, and sucks a refrigerant gas from aninlet port 30B. - Hereinafter, an operation of the refrigerant compressor configured as mentioned above is described. Firstly, the
motor 53 drives thecompression part 56, so that thepiston 68 reciprocates in thecylinder 63. A low temperature and low pressure refrigerant gas returning from an external refrigerating cycle (not shown) is firstly sucked into thehermetic container 51 from thesuction tube 52. The refrigerant gas is further sucked from theinlet port 30B of thesuction muffler 30 and passes through thesuction hole 65 via the communicatingtube 30A. During the suction stroke, by flexing thedeformation part 67A of thevalve 67, the refrigerant gas opens thevalve 67 and is led to thecylinder 63. During the compression stroke, thevalve 67 is closed. Thus, the refrigerant gas is compressed to high temperature and high pressure, passes from thedischarge hole 66 through a discharge tube (not shown) and is led to the external refrigerating cycle (not shown) so as to be used for a refrigerating operation. - At this time, the
valve 67 is so designed as to have a natural frequency for carrying out an opening and closing operation with good timing in accordance with a low-speed operation frequency. Therefore, the compressor is capable of operation with a reduced suction loss and a high volumetric efficiency. - However, when a low-speed operation frequency is changed to a high-speed operation frequency due to the change in cooling load conditions, the timing of opening and closing operation determined by the natural frequency of the
valve 67 is off. At this time, even when the pressure in thecylinder 63 exceeds the pressure in thesuction space 61A of thecylinder head 61, thevalve 67 does not complete a closing operation. Consequently, delayed closing occurs, causing a backflow of a refrigerant gas, so that the volumetric efficiency is lowered and the refrigerating capacity and the refrigerating efficiency are lowered. - As a solution to reduce the backflow of a refrigerant gas due to delayed closing of the
valve 67, designing thevalve 67 to have a high natural frequency in accordance with the high-speed operation is considered. In this case, since the spring constant of thedeformation part 67A is increased, an amount of flexure is reduced, so that the suction loss is increased and accordingly the refrigerating capacity and the refrigerating efficiency are lowered. - The refrigerant compressor of the present invention includes a piston, a cylinder and a valve plate. The valve plate is provided at an opening end of the cylinder and includes a plurality of suction holes. The refrigerant compressor of the present invention further includes a plurality of suction reed valves, which is provided between the opening end of the cylinder and the valve plate, for opening and closing the plurality of suction holes, respectively. At least one of the suction reed valves has a natural frequency different from that of the other reed valves. With this configuration, even when an operation frequency is changed, delayed closing of the suction reed valve and reduction in an amount of flexure are prevented.
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- FIG. 1 is a sectional view showing a refrigerant compressor in an embodiment of the preset invention.
- FIG. 2 is a front view showing a suction reed valve of the refrigerant compressor shown in FIG. 1.
- FIG. 3 is a sectional view showing a cylinder head part of the refrigerant compressor shown in FIG. 1.
- FIG. 4 is a graph showing a pressure in a cylinder and an amount of flexure of a reed valve in one stroke in a low-speed operation of a refrigerant compressor in an embodiment of the present invention.
- FIG. 5 is a graph showing a pressure in a cylinder and an amount of flexure of a reed valve in one stroke in a high-speed operation of a refrigerant compressor in an embodiment of the present invention.
- FIG. 6 is a sectional view showing a conventional refrigerant compressor.
- FIG. 7 is an exploded perspective view showing a valve of the refrigerant compressor of FIG. 6.
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- FIG. 1 is a sectional view showing a refrigerant compressor in an embodiment of the preset invention. FIG. 2 is a front view showing a suction reed valve. FIG. 3 is a sectional view showing a cylinder head part.
- To a
hermetic container 1, anoutlet port 2A that is one end of asuction tube 2 is connected. Another end of thesuction tube 2 is connected to a piping at the low-pressure side of a refrigerating cycle (not shown). Amotor 3 includes astator 4 and arotor 5, and drives acompression part 6. Furthermore, refrigeratingmachine oil 7 is preserved in a bottom portion of thehermetic container 1. A coil spring 8 elastically supports themotor 3 and thecompression part 6. - The
compression part 6 includes acylinder head 101, acylinder block 12, avalve plate 110, suction reed valves (hereinafter, referred to as "valve") 120A and 120B, apiston 18, a connectingrod 20 and asuction muffler 130. Thecylinder head 101 forms asuction space 101A and adischarge space 101B. Thecylinder block 12 contains acylinder 13. The connectingrod 20 is linked to aneccentric part 19A of acrank shaft 19. Thesuction muffler 130 communicates to asuction space 101A via a communicatingtube 130A and tosuction holes valve plate 110, and sucks a refrigerant gas from aninlet port 130B. - The
valve plate 110 has thesuction holes suction holes opening portions valve plate 110 at the side of thecylinder 13 to openingportions valve plate 110 at the side ofcylinder head 101 in the direction in which a distance between the suction holes is reduced. Thevalves deformation parts deformation part 122A is longer than thedeformation part 122B, the spring constant of thevalve 120A is smaller, and thevalve 120A has a lower natural frequency than that of thevalve 120B. Furthermore, the shapes of thevalves centerlines deformation parts points valves -
Seal parts valve plate 110. - Hereinafter, an operation of the refrigerant compressor configured as mentioned above is described. FIG. 4 is a graph showing a pressure in a cylinder and an amount of flexure of a reed valve in one stroke in a low-speed operation of a refrigerant compressor in an embodiment of the present invention. FIG. 5 is a graph showing a pressure in a cylinder and an amount of flexure of a reed valve in one stroke in a high-speed operation of a refrigerant compressor in an embodiment of the present invention.
- The
motor 3 drives thecompression part 6, so that thepiston 18 reciprocates in thecylinder 13. A low temperature and low pressure refrigerant gas returning from an external refrigerating cycle (not shown) is firstly sucked into thehermetic container 1 from thesuction tube 2. The refrigerant gas is further sucked from theinlet port 130B of thesuction muffler 130 and passes through the suction holes 112A and 112B via the communicatingtube 130A. During the suction stroke, by flexing thedeformation parts valves valve cylinder 13. During the compression stroke, thevalves - When the
piston 18 reciprocates in thecylinder 13, in the suction stroke, thepiston 18 shifts to the side of a bottom dead center. In a low-speed operation, in this suction stroke, gas pressure load, which is generated by differential pressure when thepressure 140 in thecylinder 13 becomes lower than the pressure in thesuction space 101A of thecylinder head 101, acts on thevalves point 140A, thesuction reed valves cylinder 13. Thepoint 140A means a point at which the gas pressure load generated by differential pressure becomes larger than a resultant force of flexure load of thevalves 120A-120B and an adhesion force with the viscosity of refrigerating machine oil at the seal parts of thevalves 120A-120B. - Furthermore, in the compression stroke, the
valves point 140B at which the pressure in thecylinder 13 exceeds the pressure in thesuction space 101A of thecylinder head 101, and suction of the refrigerant gas from thesuction muffler 130 is completed. - Between the
point 140A and thepoint 140B, thevalve 120A repeats opening andclosing operations 150A twice at a natural frequency in primary deformation mode while flexing thedeformation part 122A. Since thevalve 120A is selected to have a natural frequency corresponding to a low-speed operation frequency, thevalve 120A completes closing substantially with the same timing as thepoint 140B. Furthermore, since the spring constant of thevalve 120A is small, even under conditions that the flow rate of sucked gas is slow during a low-speed operation, a suction loss due to the shortage of an amount of flexure is not increased. - Furthermore, the
valve 120B has a natural frequency and a spring constant higher than those of thevalve 120A, and repeats opening and closingoperations 150B four times between thepoint 140A and thepoint 140B. At this time, thevalve 120B opens widely with a certain amount of flexure according to the circulation amount of refrigerant at the first to third opening and closingoperations 150B. At the fourth opening and closing operation, since in the compression stroke, the differential pressure between the pressure in thecylinder 13 and the pressure in thesuction space 101A of thecylinder head 101 is extremely small. At this time, the refrigerant gas flows in thesuction hole 112A of thevalve 120A that flexes more largely. Consequently, the amount of a refrigerant gas flowing in thesuction hole 112B of thevalve 120B becomes very small and the dynamic pressure by the flow of the refrigerant gas is reduced. That is to say, thevalve 120B hardly flexes and it completes opening and closing operation near thepoint 141B. - Therefore, backflow of the refrigerant gas due to delayed closing of the
valves - Furthermore, in a high-speed operation, between the
point 141A and thepoint 141B, thevalve 120B repeats opening and closingoperations 151B three times and flexes with a certain amount of flexure according to the circulation amount of refrigerant, and then completes closing with good timing. Thepoint 141A means a point at which the pressure in thecylinder 13 becomes lower than the pressure in thesuction space 101A of thecylinder head 101. Furthermore, thepoint 141B means a point at which the pressure in thecylinder 13 exceeds the pressure in thesuction space 101A of thecylinder head 101. - The
valve 120A opens widely in a certain amount of flexure according to the circulation amount of refrigerant at the first opening andclosing operation 151A. On the other hand, in the second opening and closing operation, since in a compression stroke, the differential pressure between the pressure in thecylinder 13 and the pressure in thesuction space 101A of thecylinder head 101 is extremely small. Therefore, the refrigerant gas passes through thesuction hole 112B of thevalve 120B that flexes more largely. Consequently, thevalve 120A hardly flexes and it completes the opening and closing operation near thepoint 141B. - Therefore, also in a high-speed operation, delayed closing or shortage of the amount of flexure of the
valves cylinder 13 efficiently. Consequently, in a case where the operation frequency is changed, the refrigerating capacity and the compression efficiency of the compressor are increased. - Furthermore, the shapes of the
valves centerlines deformation parts points valves centerlines valves valves valves circular seal parts valves machine oil 7 is concentrated, thus making it easy to open thevalves valves cylinder 13 efficiently, and the refrigerating capacity and the compression efficiency of the compressor are increased. Note here that in FIG. 2, both of the shapes of thevalves centerlines deformation parts - A refrigerant gas inside the
hermetic container 1 passes through thesuction space 101A in a high-temperature cylinder head 101 via thesuction muffler 130 and is sucked into thecylinder 13 from the suction holes 112A and 112B provided on thevalve plate 110. Herein, the refrigerant gas inside thecylinder 13 is in a high temperature state of about 100°C by a compression action and is discharged to adischarge space 101B of thecylinder head 101. Thus, thecylinder head 101 is heated to high temperature state of about 80°C. - In this case, as an interval between the two
suction holes suction space 101A in thecylinder head 101, at least a distance corresponding to a sum of the widths of theseal part 128A and theseal part 128B is necessary. Herein, as shown in FIG. 3, in a case where the suction holes 112A and 112B are inclined, it is not necessary to consider the widths of theseal part 128A and theseal part 128B, and it is possible to greatly reduce the interval between the suction holes 112A and 112B. Thus, thesuction space 101A in thecylinder head 101 can be configured to have a reduced volume and heat receiving area, so that the thermal transmission to the flowing refrigerant gas is reduced. Accordingly, the temperature of the refrigerant can be kept low, the density of the gas refrigerant increases and the circulation amount of the refrigerant increases. Consequently, the refrigerating capacity and the compression efficiency of the compressor increase. Note here that in FIG. 3, both of the suction holes 112A and 112B are inclined, but only one of them may be inclined. - Note here that in the embodiment, the number of the
valves - Furthermore, in the embodiment, the natural frequency is changed by varying the lengths of the
valves valves - Furthermore, in the embodiment, the case where the number of opening and closing operations in one stroke of the
valve - A refrigerant compressor of the present invention includes a piston, a cylinder and a valve plate. The valve plate is provided at an opening end of the cylinder and has a plurality of suction holes. The refrigerant compressor of the present invention further includes a plurality of suction reed valves provided between the opening end of the cylinder and the valve plate, and opens and closes the plurality of suction holes, respectively. At least one of the suction reed valves has a natural frequency different from that of the other reed valves. With this configuration, since refrigerating capacity and compression efficiency of the refrigerant compressor can be increased, the refrigerant compressor can be used for air conditioners, freezer-refrigerators, and the like.
Claims (3)
- A refrigerant compressor, comprising:a piston;a cylinder housing the piston;a valve plate, which has a first suction hole and a second suction hole, provided at an opening end of the cylinder;a first suction reed valve, which opens and closes the first suction hole, provided between the opening end of the cylinder and the valve plate; anda second suction reed valve, which opens and closes the second suction hole and has a natural frequency different from that of the first reed valve, provided between the opening end of the cylinder and the valve plate.
- The refrigerant compressor according to claim 1, wherein the first suction reed valve has a first deformation part and the second suction reed valve has a second deformation part, at least one of a shape of the first suction reed valve being asymmetric with respect to a centerline of the first deformation part and a shape of the second suction reed valve being asymmetric with respect to a centerline of the second deformation part.
- The refrigerant compressor according to claim 1, wherein at least one of the first suction hole and the second suction hole is inclined from an opening end face of the valve plate at the cylinder to another end face in the direction in which an interval between the first suction hole and the second suction hole is reduced.
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003133120 | 2003-05-12 | ||
JP2003133120 | 2003-05-12 | ||
JP2004120162 | 2004-04-15 | ||
JP2004120162A JP2004360686A (en) | 2003-05-12 | 2004-04-15 | Refrigerant compressor |
PCT/JP2004/006578 WO2004099617A1 (en) | 2003-05-12 | 2004-05-10 | Refrigerant compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1541868A1 true EP1541868A1 (en) | 2005-06-15 |
EP1541868A4 EP1541868A4 (en) | 2005-12-14 |
Family
ID=33436441
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04732026A Withdrawn EP1541868A4 (en) | 2003-05-12 | 2004-05-10 | Refrigerant compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US20060039808A1 (en) |
EP (1) | EP1541868A4 (en) |
JP (1) | JP2004360686A (en) |
KR (1) | KR20050033613A (en) |
WO (1) | WO2004099617A1 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2895037A1 (en) * | 2005-12-20 | 2007-06-22 | Tecumseh Europ S A Sa | VALVE DEVICE FOR FLUID COMPRESSOR AND FLUID COMPRESSOR |
CN104619987A (en) * | 2012-09-13 | 2015-05-13 | 艾默生环境优化技术有限公司 | Compressor assembly with directed suction |
US11236748B2 (en) | 2019-03-29 | 2022-02-01 | Emerson Climate Technologies, Inc. | Compressor having directed suction |
US11248605B1 (en) | 2020-07-28 | 2022-02-15 | Emerson Climate Technologies, Inc. | Compressor having shell fitting |
US11619228B2 (en) | 2021-01-27 | 2023-04-04 | Emerson Climate Technologies, Inc. | Compressor having directed suction |
US11767838B2 (en) | 2019-06-14 | 2023-09-26 | Copeland Lp | Compressor having suction fitting |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4701789B2 (en) * | 2005-03-30 | 2011-06-15 | パナソニック株式会社 | Hermetic compressor |
JP2010127100A (en) * | 2008-11-25 | 2010-06-10 | Daikin Ind Ltd | Delivery valve and rotary compressor |
US8747083B2 (en) * | 2010-11-16 | 2014-06-10 | Wen San Chou | Air compressor having enlarged compartment for receiving pressurized air |
BRPI1101993A2 (en) * | 2011-04-28 | 2014-02-11 | Whirlpool Sa | Valve Arrangement for Hermetic Compressors |
BRPI1105143B1 (en) * | 2011-12-15 | 2021-07-27 | Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda | SUCTION VALVE ASSEMBLY FOR ALTERNATIVE COMPRESSOR |
AT17214U1 (en) * | 2019-12-19 | 2021-09-15 | Anhui meizhi compressor co ltd | Hermetically sealed refrigerant compressor |
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- 2004-05-10 EP EP04732026A patent/EP1541868A4/en not_active Withdrawn
- 2004-05-10 US US10/522,514 patent/US20060039808A1/en not_active Abandoned
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Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2895037A1 (en) * | 2005-12-20 | 2007-06-22 | Tecumseh Europ S A Sa | VALVE DEVICE FOR FLUID COMPRESSOR AND FLUID COMPRESSOR |
WO2007071665A1 (en) * | 2005-12-20 | 2007-06-28 | Tecumseh Europe S.A. | System of valves for a fluid compressor and fluid compressor |
CN104619987A (en) * | 2012-09-13 | 2015-05-13 | 艾默生环境优化技术有限公司 | Compressor assembly with directed suction |
EP2909480A4 (en) * | 2012-09-13 | 2016-06-29 | Emerson Climate Technologies | Compressor assembly with directed suction |
US10094600B2 (en) | 2012-09-13 | 2018-10-09 | Emerson Climate Technologies, Inc. | Compressor assembly with directed suction |
US10928108B2 (en) | 2012-09-13 | 2021-02-23 | Emerson Climate Technologies, Inc. | Compressor assembly with directed suction |
US10995974B2 (en) | 2012-09-13 | 2021-05-04 | Emerson Climate Technologies, Inc. | Compressor assembly with directed suction |
US11236748B2 (en) | 2019-03-29 | 2022-02-01 | Emerson Climate Technologies, Inc. | Compressor having directed suction |
US11767838B2 (en) | 2019-06-14 | 2023-09-26 | Copeland Lp | Compressor having suction fitting |
US11248605B1 (en) | 2020-07-28 | 2022-02-15 | Emerson Climate Technologies, Inc. | Compressor having shell fitting |
US11619228B2 (en) | 2021-01-27 | 2023-04-04 | Emerson Climate Technologies, Inc. | Compressor having directed suction |
Also Published As
Publication number | Publication date |
---|---|
WO2004099617A1 (en) | 2004-11-18 |
JP2004360686A (en) | 2004-12-24 |
KR20050033613A (en) | 2005-04-12 |
US20060039808A1 (en) | 2006-02-23 |
EP1541868A4 (en) | 2005-12-14 |
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