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
  • F04B39/0005—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
• • 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
• • 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
• • 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
• • 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
• • 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 the efficiency of a hermetic compressor used for a freezing and refrigeration apparatus.
• hermetic compressors used in freezers and the like have been strongly desired.
• Conventional hermetic compressors improve the compression efficiency by, for example, increasing the suction efficiency by using two suction holes in the valve unit in the compression section.
• Such a compressor is disclosed in, for example, Japanese Patent Application Laid-Open No. 3-175174.
• an example of a conventional hermetic compressor will be described with reference to the drawings.
• FIG. 6 is a sectional view of a conventional refrigerant compressor
• FIG. 7 is an exploded perspective view of a valve of the conventional refrigerant compressor.
• An outlet 52A which is one end of a suction pipe 52, is connected to the closed vessel 51, and the other end of the suction pipe 52 is connected to a low-pressure side pipe (not shown) of the refrigeration cycle.
• the motor 53 is composed of a stator 54 and a rotor 55, and drives the compression unit 56.
• Refrigeration oil 57 is stored at the bottom of the sealed container 51.
• the coil spring 58 elastically supports the module 53 and the compression section 56.
• the compression section 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 3.
• the cylinder head 61 forms a suction space 61A and a discharge space 61B.
• the cylinder block 62 has a cylinder 63.
• the valve plate 64 has two suction holes 65 and two discharge holes 66.
• the suction reed valve (hereinafter, valve) 67 has a deformed portion 67A.
• the connecting rod 70 is connected to the eccentric part 69 A of the crank shaft 69.
• the suction muffler 30 is connected to the suction space 61A via the communication pipe 30A and the suction hole of the valve plate 64. Communicates with 65 and draws refrigerant gas from the inlet 30B.
• the compression section 56 is driven by the motor 53, and the piston 68 reciprocates in the cylinder 63.
• the low-temperature and low-pressure refrigerant gas returned from the external refrigeration cycle (not shown) is first drawn into the closed vessel 51 from the suction pipe 52.
• the refrigerant gas is further sucked from the inlet 30B of the suction muffler 30 and passes through the suction hole 65 through the communication pipe 3OA.
• the coolant gas is guided to the cylinder 63 by opening the valve 67.
• valve 67 is closed, and the refrigerant gas is compressed to a high temperature and high pressure, passes through the discharge port 66, passes through a discharge pipe (not shown), and is guided to an external refrigeration cycle (not shown) for refrigeration.
• valve 67 is designed to have a natural frequency that opens and closes in a timely manner in accordance with the low-speed operation frequency, so the compressor has low suction loss and can operate with high volumetric efficiency. .
• the timing of the opening / closing operation determined by the natural frequency of the valve 67 will be shifted. At this time, even if the pressure in the cylinder 63 exceeds the pressure in the suction space 61A of the cylinder head 61, the valve 67 does not complete the closing operation. As a result, the refrigerant gas flows backward due to the delay in closing and the volume efficiency is reduced, and the refrigeration capacity and refrigeration efficiency are reduced.
• a refrigerant compressor according to the present invention includes a piston, a cylinder, and a valve plate.
• the valve plate is provided at the open end of the cylinder. It has a number of suction holes.
• the refrigerant compressor according to the present invention further has a plurality of suction lead valves provided between the open end of the cylinder and the valve plate to open and close the plurality of suction holes, respectively. At least one of the suction reed valves has a different natural frequency than the other reed valves. With this configuration, even if the operating frequency changes, a delay in closing the suction reed valve and a decrease in the amount of deflection are prevented.
• FIG. 1 is a sectional view of a refrigerant compressor according to an embodiment of the present invention.
• FIG. 2 is a front view of a suction reed valve in the refrigerant compressor of FIG.
• FIG. 3 is a cross-sectional view of a cylinder head of the refrigerant compressor of FIG. 1.
• FIG. 4 is a cylinder pressure and a reed valve deflection during one stroke in a low-speed operation of the refrigerant compressor according to the embodiment of the present invention.
• FIG. 5 is a diagram showing the pressure in the cylinder and the amount of deflection of the reed valve during one stroke in the high-speed operation of the refrigerant compressor in the embodiment of the present invention.
• FIG. 6 is a sectional view of a conventional refrigerant compressor.
• FIG. 7 is an exploded perspective view of a valve of the refrigerant compressor of FIG. BEST MODE FOR CARRYING OUT THE INVENTION
• FIG. 1 is a cross-sectional view of a refrigerant compressor according to an embodiment of the present invention.
• FIG. 2 is a front view of the suction reed valve.
• Fig. 3 is a sectional view of the cylinder head.
• An outlet 2A which is one end of a suction pipe 2, is connected to the closed vessel 1, and the other end of the suction pipe 2 is connected to a low-pressure side pipe (not shown) of the refrigeration cycle.
• the motor 3 includes a stator 4 and a rotor 5 and drives a compression unit 6.
• the refrigerating machine oil 7 is stored at the bottom of the closed container 1.
• the coil spring 8 elastically supports the motor 3 and the compression section 6.
• the compression unit 6 includes a cylinder head 101, a cylinder block 12 and It is composed of a valve plate 110, a suction reed valve (hereinafter, a valve) 120A, 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 has a cylinder 13.
• the connecting rod 20 is connected to the eccentric part 19 A of the crankshaft 19.
• the suction muffler 130 communicates with the suction space 110 A through the pipe 13 OA, and communicates with the suction holes 1 12 A and 1 12 B of the valve plate 110, and the inlet section 130 B More refrigerant gas is sucked.
• the valve plate 110 has suction holes 112A and 112B and a discharge hole (not shown).
• Suction holes 1 1 2 A, 1 1 2 B are openings 1 1 4 from cylinder 13 opening 1 1 4 A, 1 1 4 B to cylinder head 1 0 1 side of valve plate 1 1 10 Inclines to C, 114D in the direction in which the distance between them decreases.
• Valves 120A and 120B have deformed portions 122A and 122B having different lengths, respectively. Since the deformed part 122 A is longer than the deformed part 122 B, the spring constant of the valve 120 A is smaller, and the valve 120 A has a lower natural frequency than the valve 120 B. I have.
• the shapes of the valves 122A and 120B are asymmetric with respect to the center lines 124A and 124B of the deformed parts 122A and 122B.
• the positions of the center points of the suction holes 1 12 A and 1 12 B correspond to the points 1 26 and 1 26 B of the valves 1 20 A and 1 208 respectively.
• the seal portions 128 A and 128 B seal the suction holes 112 A and 112 B provided in the valve plate 110.
• FIG. 4 is a cylinder pressure and reed valve deflection diagram during one stroke in a low-speed operation of the refrigerant compressor according to the present embodiment.
• FIG. 5 is a diagram showing the pressure in the cylinder and the amount of deflection of the reed valve during one stroke in the high-speed operation of the refrigerant compressor.
• the compression section 6 is driven by the motor 3, and the piston 18 reciprocates in the cylinder 13.
• the low-temperature and low-pressure refrigerant gas returned from the external refrigeration cycle (not shown) is first drawn into the closed vessel 1 from the suction pipe 2. It is. Refrigerant gas is further sucked in from the inlet portion 130B of the suction muffler 130, and passes through the suction holes 1 12A and 112B via the communication pipe 13OA.
• the refrigerant gas opens the valves 122A and 122B and the cylinder 1 Guided to 3.
• the valves 120A and 120B are closed, and the refrigerant gas is compressed to a high temperature and pressure, passes through a discharge pipe (not shown) from the discharge port, and is led to an external refrigeration cycle to perform refrigeration.
• valves 120 A and 120 B are connected to the point at which the pressure in the cylinder 13 exceeds the pressure in the suction space 101 A of the cylinder head 101. Close with B, and the suction of refrigerant gas from suction muffler 130 is completed.
• valve 120 A performs two opening and closing operations at the natural frequency of the primary deformation mode while bending the deformation section 122 A.
• Repeat OA Since the natural frequency corresponding to the low-speed operation frequency has been selected for the valve 12OA, the valve 120A closes at almost the same timing as the point 140B.
• the spring constant of the valve 120 A is small, even under the condition where the flow rate of the intake gas is low at the time of low-speed operation, the suction loss does not increase due to the insufficient amount of deflection.
• valve 120 B the natural frequency higher than the valve 120 A, It has a spring constant and repeats four opening / closing operations 150 B between point 140 A and point 140 B.
• the valve 120B opens a large amount with a predetermined amount of flexure corresponding to the refrigerant circulation amount in the first to third opening / closing operations 150B.
• the fourth opening / closing operation the pressure difference between the inside of the cylinder 13 and the suction space 101A of the cylinder head 101 is very small because it is in the compression stroke. At this time, the refrigerant gas flows through the inlet hole 112A of the valve 120A, which is more greatly bent.
• the valve 120B completes the opening / closing operation near the point 141B with almost no bending.
• the knob 124B repeats three opening / closing operations 151B between the point 141A and the point 141B, and performs the predetermined operation according to the refrigerant circulation amount.
• Point 14 1 A is the point when the pressure in cylinder 13 drops below the pressure in cylinder head 101 suction space 101 A
• the point 141B indicates the point in time when the pressure in the cylinder 13 exceeds the pressure in the suction space 101A of the cylinder head 101.
• the valve 120 A opens a large amount with a predetermined amount of deflection corresponding to the amount of circulating refrigerant at the first opening and closing operation 15 1 A.
• the differential pressure between the inside of the cylinder 13 and the suction space 101A of the cylinder head 101 is very small because it is in the compression stroke. Therefore, after the second time, the refrigerant gas passes through the inlet hole 112B of the valve 120B, which is greatly bent. Therefore, the valve 120A completes the opening / closing operation near the point 141B with almost no bending.
• the shapes of the knobs 120A and 120B are asymmetric with respect to the center lines 124A and 124B of the deformed portions 122A and 122B. For this reason, the points of action 12 6 A, 12 B of the gas pressure load acting on the valves 12 A, 12 B and the center line of the radial deformation of the valves 12 OA, 12 OB 1 2 4 A and 1 24 B shift. As a result, the valves 120A and 120B start opening while being torsionally deformed. That is, the torsional moment caused by the gas pressure load acts on the valves 12OA and 120B.
• the force of peeling off the adhered part due to the viscosity of the refrigerating machine oil 7 acts on one side of the circular seal parts 128 A, 128 B of the valves 120 A, 120 B, and the valve 1 20 A and 120 B are easy to open. Therefore, the opening of the valves 120A and 120B in the suction stroke starts earlier. Therefore, the refrigerant gas is efficiently sucked into the cylinder 13 and the refrigeration capacity and the compression efficiency are increased.
• the shapes of the valves 120 A and 120 B are asymmetric with respect to the center lines 124 A and 124 B of the deformed parts 122 A and 122 B, respectively. However, only one may do so.
• the refrigerant gas in the sealed container 1 passes through the suction space 101 in the high-temperature cylinder head 101 via the suction muffler 130, and the suction hole 1 provided in the valve plate 110. Inhaled into cylinder 13 from 12 A and 11 B.
• the refrigerant gas in the cylinder 13 is brought into a high temperature state of about 100 by compression action and is discharged to the discharge space 101 B of the cylinder head 101.
• the cylinder head 101 is heated to a high temperature state of about 80 ° C.
• the interval between the two suction holes 1 1 2 A and 1 1 2 B of the suction space 1 0 1 A in the cylinder head 101 is at least as small as the seal 1 2 28 A and the seal 1 2 8 B Is necessary to add the width of
• the suction holes 112A and 112B are inclined as shown in Fig. 3, there is no need to consider the width between the seal part 128A and the seal part 128B, and the suction hole 1
• the interval between 12 A and 11 B can be greatly reduced.
• the volume of the suction space 101A and the heat receiving area in the cylinder head 101 can be made small, and the heat transfer to the flowing refrigerant gas is reduced.
• both the suction holes 112A and 112B are inclined, but may be provided only to one of them.
• valves 120A and 120B are two, but the same effect can be obtained with three or more valves.
• the natural frequency is changed by changing the length of the valves 120A and 120B, but the width and shape of the valves 120A and 120B are changed.
• the same effect can be obtained even if the natural frequency is changed by changing the natural frequency.
• Also in the present embodiment, the number of times of opening and closing in one stroke of the valves 120A and 120B is described as 2 to 4 times. However, the same effect can be obtained if it is performed once or more.
• a refrigerant compressor according to the present invention includes a piston, a cylinder, and a valve plate.
• the valve plate is provided at an open end of the cylinder and has a plurality of suction holes.
• the refrigerant compressor according to the present invention further includes a plurality of suction reed valves provided between the open end of the cylinder and the valve plate, and respectively opening and closing the plurality of suction holes. At least one of the suction lead valves has a different natural frequency than the other reed valves. With this configuration, the refrigeration capacity and compression efficiency of the refrigerant compressor can be increased, so that it can be applied to applications such as air conditioners and refrigeration units.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Compressor (AREA)

Priority Applications (2)

Applications Claiming Priority (4)

Publications (1)

Family

ID=33436441

Family Applications (1)

Country Status (5)

Cited By (2)

Families Citing this family (11)

Citations (6)

Family Cites Families (4)

• 2004
  • 2004-04-15 JP JP2004120162A patent/JP2004360686A/ja active Pending
  • 2004-05-10 WO PCT/JP2004/006578 patent/WO2004099617A1/ja not_active Application Discontinuation
  • 2004-05-10 KR KR1020057000992A patent/KR20050033613A/ko not_active Application Discontinuation
  • 2004-05-10 US US10/522,514 patent/US20060039808A1/en not_active Abandoned
  • 2004-05-10 EP EP04732026A patent/EP1541868A4/de not_active Withdrawn

Patent Citations (6)

Non-Patent Citations (1)

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