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
  • F04B39/0027—Pulsation and noise damping means
  • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
  • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
• • 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
  • F04B35/045—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 using solenoids
• • 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
  • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
  • F04B39/123—Fluid connections

Definitions

• the present invention relates to a reciprocating compressor wherein refrigerant is sucked into through an inner space of the moving member and compressed in a compression space defined between a stationary member and a moving member, as the moving member reciprocates linearly inside the stationary member, and more particularly, to a reciprocating compressor wherein a backflow of refrigerant is prevented in an inner space of a moving member before the refrigerant is introduced from the inner space of the moving member to a compression space.
• a compression space into/from which an operation gas is sucked and discharged is defined between a piston and a cylinder, and the piston reciprocates linearly inside the cylinder to compress the refrigerant.
• the reciprocating compressor includes a component for converting a rotation force of a driving motor into a linear reciprocation force of the piston, such as a crank shaft, a large mechanical loss is caused by the motion conversion. Recently, a linear compressor has been developed to solve the above problem.
• the linear compressor a piston is coupled directly to a linearly- re ⁇ prccating linear motor, so that a mechanical loss caused by the motion conversion is prevented. Therefore, the linear compressor can improve the compression efficiency and simplify the configuration.
• power inputted to the linear motor is regulated to control an operation of the linear motor, so that noise is less generated than in the other compressors. Accordingly, the linear compressor has been mostly used in an electric home appliance installed in an indoor space, such as a refrigerator.
• FIG. 1 is a view illustrating one example of a conventional reciprocating compressor
• FIG. 2 is a view illustrating one example of a refrigerant suction passage of the conventional reciprocating compressor.
• a structure composed of a frame 1, a stationary member 2, a moving member 3, a suction valve 4, a discharge valve assembly 5, a linear motor 6, a motor cover 7, a supporter 8, a main body cover 9, a buffering spring (not shown) and a muffler assembly 10 is installed inside a shell (not shown) to be elastically supported.
• the stationary member 2 is formed in a hollow shape with both open ends.
• the discharge valve assembly 5 includes a discharge valve 5a, a discharge cap 5b and a discharge valve spring 5c. After vibration and noise of refrigerant discharged from the discharge cap 5b are suppressed through a loop pipe (not shown), the refrigerant is discharged to the outside through an outflow tube (not shown) on the side of the shell.
• the moving member 3 is formed in a hollow shape with one blocked end.
• the blocked end of the moving member 3 is inserted into the stationary member 2.
• a compression space P is defined between the stationary member 2 and the moving member 3.
• a plurality of suction holes 3a are formed in the blocked end of the moving member 3 so that refrigerant can be suked into the compression spase P therethrough.
• a groove 3b is formed in a center of the blocked end of the moving member 3 so that the thin suction valve 4 can be boMastened B thereto.
• the suction holes 3a may be formed eccentrically to one side of the blocked end of the moving member 3 as seen in the drawing, or may be formed in the center of the blocked end of the moving member 3.
• the suction valve 4 must be fixed to a rim of the moving member 3 unlike the drawing.
• a special means such as a magnet is necessary to install the suction valve 4. Accordingly, normally, the suction holes 3 a are formed eccentrically in the blocked end of the moving member 3, and the suction valve 4 is mechanically coupled to the center of the blocked end of the moving member 3 by means of a bolt or the like.
• the suction valve 4 opens and closes the suction holes 3 a of the moving member 3 by relative pressure variations of the compression space P caused by the linear reciprocation of the moving member 3.
• the linear motor 6 includes a cylindrical inner stator 6a fixed to the outside of the stationary member 2, an outer stator 6b having a predetermined interval with the inner stator 6a in a radius direction with one end supported on the frame 1 and with the other end supported on the motor cover 7 a radius, a permanent magnet 6c installed between the inner stator 6a and the outer stator 6b with a predetermined gap, and a connection member 6d for connecting the moving member 3 to the permanent magnet 6c.
• the inner stator 6a is formed by stacking laminations in a circumference direction
• the outer stator 6b is formed by mounting core blocks on a coil winding in a circumference direction at predetermined intervals. Therefore, when power is supplied from the outside to the outer stator 6b, the inner stator 6a, the outer stator 6b and the permanent magnet 6c generate a mutual electromagnetic force, so that the permanent magnet 6c and the moving member 3 connected thereto reciprocate linearly in an axis direction.
• the motor cover 7 supports the outer stator 6b in an axis direction to fix the outer stator 6b, and is bolt-fixed to the frame 1.
• the main body cover 9 is coupled to the motor cover 7.
• the supporter 8 connected to the other end of the moving member 3 is installed between the motor cover 7 and the main body cover 9 to be elastically supported by resonance springs in an axis direction.
• the supporter 8 includes a supporting protrusion 8a fitted into the springs to elastically support the springs in a motion direction of the moving member 3, a bolt hole 8b bolt-fixed B to a flange 3 c formed on the other end of the moving member 3, and an opening portion formed in a center to mount the muffler assembly 10 thereon.
• a predetermined suction hole is formed in the main body cover 9 so that refrigerant introduced from an inflow tube on the side of the shell can pass therethrough.
• the muffler assembly 10 is formed to extend lengthwise in a motion direction of the moving member 3.
• the muffler assembly 10 not only guides a suction flow of the refrigerant but also attenuates noise generated when the refrigerant is sucked into the compression space P through the siction valve 4.
• noise can be attenuated according to an acoustic characteristic.
• the muffler assembly 10 includes the sound attenuation duct 11 extended lengthwise in an axis direction inside the moving member 3, a hollow outer casing 12 formed on the outside of the other end of the moving member 3, an inner extension duct 13 formed inside an inlet of the outer casing 12, the resonance chamber 14 defining a space with a large inner volume inside the outer casing 12, and having an opening portion so that refrigerant can pass therethrough, and a mounting portion 15 extended in a radius direction and bolt-fixed B to the flange 3 c of the moving member 3.
• the muffler assembly 10 is bolt-fixed B to the flange 3c of the moving member 3 with the supporter 8.
• An object of the present invention is to provide a reciprocating compressor capable of reducing a backflow of refrigerant introduced from a muffler assembly to a suction hole of a moving member.
• Another object of the present invention is to provide a reciprocating compressor capable of reducing a flow loss of refrigerant introduced from a muffler assembly to a suction hole of a moving member.
• a further object of the present invention is to provide a reciprocating compressor capable of maximizing the noise attenuation efficiency of a muffler assembly by increasing a length of a sound attenuation duct of the muffler assembly as mvch as possible in a given condition.
• a reciprocating compressor comprising: a hollow stationary member; a moving member reciprocating linearly inside the stationary member, and having a suction hole in a blocked end so that refrigerant can be introduced therethrough; a sound attenuation duct extended lengthwise inside the moving member to guide introduced refrigerant; and a backflow prevention portion expanded from an end of the sound attenuation duct toward the moving member to prevent a backflow of the refrigerant.
• the suction hole may be formed eccentrically in the blocked end of the moving member.
• the reciprocating compressor comprises a muffler assembly including the sound attenuation dust and a resonance chamber communicating with the sound attenuation duct so as to attenuate noise generated due to the inflow of the refrigerant.
• the sound attenuation duct may be formed at an inner center of the moving member to extend lengthwise in a longitudinal direction of the moving member, and the resonance chamber may be formed outside the moving member to communicate with the sound attenuation duct.
• the backflow prevention portion may be formed in a flange shape to expand perpendicularly from an end of the sound attenuation duct toward an inner surface of the moving member, may be formed in a funnel shape with a diameter increased in an axis direction at an end of the sound attenuation duct, or may be formed in a cup shape to expand from an end of the sound attenuation duct with a step difference.
• the backflow prevention portion may be formed as one body with the sound attenuation duct by using a plastic material, or made of a steel material and welded to an end of the sound attenuation duct.
• an end of the backflow prevention portion contacts closely to an inner surface of the moving member.
• FIG. 1 is a view illustrating one example of a conventional reciprocating compressor.
• FIG. 2 is a view illustrating one example of a refrigerant suction passage of the conventional reciprocating compressor.
• FIGS. 3 to 5 are views illustrating various embodiments of a refrigerant suction passage of a reciprocating compressor according to the present invention. Mode for the Invention
• FIGS. 3 to 5 are views illustrating various embodiments of a refrigerant suction passage of a reciprocating compressor according to the present invention.
• suction holes 103 a are formed eccentrically in one blocked end of a moving member 103 to communicate with a compression space P defined between a stationary member (not shown) and the moving member 103, and a supporter 108 and a muffler assembly 110 are installed at the other end of the moving member 103.
• a sound attenuation duct 111 of the muffler assembly 110 is positioned at an inner center of the moving member 103, and a backflow prevention portion 116 is formed at an end of the sound attenuation duct 111 to expand in a radius direction.
• the moving member 103 is formed in a piston shape, and the suction holes
• a bolt groove 103b is formed in a center of the blocked end so that a thin suction valve (not shown) for opening and closing the suction holes 103a can be bolt-fixed thereto.
• a flange 103c is formed at the open end of the moving member 103 to expand in a radius direction, and the supporter 108 and the muffler assembly 110 are bolt- fixed B to the flange 103 c of the moving member 103.
• the supporter 108 includes a supporting protrusion 108a and a bolt hole 108b
• the muffler assembly 110 includes the sound attenuation duct 111, an outer casing 112, an inner extension duct 113, a resonance chamber 114 and a mounting portion 115. Therefore Detailed explanations thereof are omitted.
• the badcflow prevention portion 116 is formed in a flange shape to expand perpendicularly from the end of the sound attenuation diet 111 of the muffler assembly 110 toward the inner surface of the moving member 103, namely, in a radius direction.
• the badcflow prevention portion 116 serves to guide refrigerant passing through the sound attenuation duct 111 toward the suction holes 103a
• the sound attenuation diet 111 of the muffler assembly 110 can be formed longer than in the prior art, namely, the sound attenuation duct 111 can be formed closer to the blocked end of the moving member 103.
• the sound attenuation diet 111 is relatively longer than in the prior art, thereby improving the noise attenuation characteristic.
• the backflow prevention portion 116 is expanded from the sound attenuation dust 111 of the muffler assembly
• the backflow prevention portion 116 may be injection-molded with the sound attenuation duct 111 by using the plastic material. Meanwhile, if the sound attenuation duct 111 is made of a steel material, the backflow prevention portion 116 may be separately made of a steel material, and fixed to the end of the sound attenuation duct 111 by means of welding such as brazing.
• the refrigerant passing through the sound attenuation duct 111 of the muffler assembly 110 moves along the inner center of the moving member 103.
• Some refrigerant flows directly into the suction holes 103a of the moving member 103.
• the refrigerant moves along the inner suface of the moving member 103, collides against the backflow prevention portion 116, and flows toward the suction holes 103a again in a refrigerant flow direction.
• a second embodiment of the refrigerant suction passage of the reciprocating compressor according to the present invention is identical to the first embodiment described above.
• a backflow prevention portion 117 is formed in a funnel shape with a diameter increased in a refrigerant flow direction at an end of a sound attenuation dirt 111 of a muffler assembly 110, and an end of the backflow prevention portion 117 contact closely to an inner diameter of a moving member 103.
• the badcflow prevention portion 117 serves to guide refrigerant passing through the sound attenuation duct 111 toward suction holes 103a
• the sound attenuation duct 111 of the muffler assembly 110 can be formed longer than in the prior art, namely, the sound attenuation duct 111 can be formed closer to the blocked end of the moving member 103. Accordingly, the sound attenuation duct 111 is relatively longer than in the prior art, thereby improving the noise attenuation characteristic.
• the sound attenuation duct 111 of the muffler assembly 110 is not longer than in the prior art, as the backflow prevention portion 117 is gradually expanded in a radius direction of the sound attenuation duct 111 of the muffler assembly 110 along a refrigerant flow direction, the suction holes 103 a of the moving member 103 and the backflow prevention portion 117 are formed adjacent to each other.
• the badcflow prevention portion 117 may be formed as one body with the sound attenuation duct 111 of the muffler assembly 110 by using a plastic material, or made of a steel material and welded to the sound attenuation duct 111 of the muffler assembly 110.
• the refrigerant passing through the sound attenuation duct 111 of the muffler assembly 110 moves along the inner center of the moving member 103. Some refrigerant flows directly into the suction holes 103 a of the moving member 103. Even if the other refrigerant collides against the blocked end of the moving member 103 and flows backward, the refrigerant is guided by the inner diameter of the moving member 103 and the backflow prevention portion 117, pins the refrigerant passing through the sound attenuation duct 111, and flows toward the suction holes 103a in a refrigerant flow direction.
• a third embodiment of the refrigerant suction passage of the reciprocating compressor according to the present invention is identical to the second embodiment described above.
• a backflow prevention portion 118 is formed in a cup shape to expand from an end of a sound attenuation duct 111 of a muffler assembly 110, and an end of the backflow prevention portion 118 contacts closely to an inner surface of a moving member 103.
• the backflow prevention portion 118 is formed longer in a refrigerant flow direction, maintaining a gap therefrom.
• the sound attenuation duct 111 of the muffler assembly 110 is not longer than in the prior art, as the backflow prevention portion 118 is expanded perpendicularly in a radius direction of the sound attenuation duct 111 of the muffler assembly 110 and extended in a refrigerant flow direction, suction holes 103 a of the moving member 103 and the backflow prevention portion 118 are formed adjacent to each other.
• the backflow prevention portion 118 may be formed as one body with the sound attenuation duct 111 of the muffler assembly 110 by using a plastic material, or made of a steel material and welded to the sound attenuation duct 111 of the muffler assembly 110.
• the muffler assembly 110 flows directly into the suction holes 103 a of the moving member 103. Even if the other refrigerant collides against the blocked end of the moving member 103 and flows backward, the refrigerant is guided by the inner diameter of the moving member 103 and the backflow prevention portion 118, pins the refrigerant passing through the sound attenuation duct 111, and flows along the moving member 103 in a refrigerant flow direction.
• a flow rate of refrigerant flowing bakward is associated closely with a structure of a refrigerant flow passage. It is represented as follows.
• the flow rate Qb of the refrigerant flowing backward is proportional to a pressure difference ⁇ P between a pressure of a space formed between the sound attenuation duct 111 and the moving member 103 and a pressure of an outlet portion of the backflow prevention portion 116, 117 or 118, and a gap h between the inner surface of the moving member 103 and the badcflow prevention portion 116, 117 or 118, but inversely proportional to a flow direction length L of the sound attenuation diet 111 and the badcflow prevention portion 116, 117 or 118.
• the gap h between the inner suface of the moving member 103 and the backflow prevention portion 116, 117 or 118 is reduced as much as possible on the basis of the above formula, thereby minimiang the flow rate of the refrigerant flowing backward. That is, according to the present invention, preferably, the end of the backflow prevention portion 116, 117 or 118 is in contact with the inner suface of the moving member 103 to minimize the gap h.
• the length of the sound attenuation duct 111 is increased or the refrigerant flow direction length is increased at the end of the sound attenuation duct 111 in the refrigerant flow direction so that the backflow prevention portion 116, 117 or 118 can approach the suction holes 103 a of the moving member 103 as close as possible. Therefore, the refrigerant less flows backward or does not flow backward, and the flow loss of the refrigerant does not occur. Accordingly, as described above, if the length of the sound attenuation duct 111 increases, the noise attenuation efficiency can be improved.
• the flow rate of the refrigerant circulated in each embodiment of the reciprocating compressor according to the present invention can be increased to improve the compression efficiency and to subsequently improve an energy efficiency ratio (EER).
• EER energy efficiency ratio
• the EERS of the first to third embodiments have been improved by 0.08, 0.07 and 0.1, respectively.
• the present invention in a reciprocating compressor, even if a backflow of refrigerant occurs before the refrigerant is introduced from a sound attenuation duct of a muffler assembly to a suction hole of a moving member, the refrigerant collides against a backflow prevention portion formed at an end of the sound attenuation duct of the muffler assembly, and is guided to flow again toward the suction hole of the moving member. It is thus possible to suppress the backflow of the refrigerant.
• the backflow prevention portion is attached between an inner diameter of the moving member and the sound attenuation duct of the muffler assembly, a flow loss of the refrigerant caused by the backflow is prevented before the refrigerant is introduced into a compression space. It is therefore possible to increase a flow rate of the refrigerant. Further, a length of the sound attenuation duct is increased to improve the noise attenuation efficiency and to subsequently improve the compression efficiency and the energy efficiency.

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

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• 2007
  • 2007-12-21 WO PCT/KR2007/006759 patent/WO2008082116A2/en active Application Filing
  • 2007-12-21 KR KR1020070135656A patent/KR20080063706A/ko active Search and Examination
  • 2007-12-21 CN CN2007800489849A patent/CN101589231B/zh not_active Expired - Fee Related

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