WO2022173138A1 - Compresseur linéaire - Google Patents

Compresseur linéaire Download PDF

Info

Publication number
WO2022173138A1
WO2022173138A1 PCT/KR2022/000890 KR2022000890W WO2022173138A1 WO 2022173138 A1 WO2022173138 A1 WO 2022173138A1 KR 2022000890 W KR2022000890 W KR 2022000890W WO 2022173138 A1 WO2022173138 A1 WO 2022173138A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat dissipation
oil
shell
cylinder
dissipation fins
Prior art date
Application number
PCT/KR2022/000890
Other languages
English (en)
Korean (ko)
Inventor
이균영
김주형
이혁
오원식
Original Assignee
엘지전자 주식회사
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 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Publication of WO2022173138A1 publication Critical patent/WO2022173138A1/fr

Links

Images

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
    • 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
    • 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
    • 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
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • 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
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a

Definitions

  • the present invention relates to a linear compressor, and more particularly, to a linear compressor having a structure for preventing a decrease in compression efficiency due to overheating of a suction temperature.
  • the compressor may be classified into a reciprocating compressor, a rotary compressor, and a scroll compressor according to a method of compressing a refrigerant.
  • the reciprocating compressor is a method in which a compression space is formed between the piston and the cylinder and the piston moves linearly to compress the fluid. It is a method of compressing the fluid by rotating a pair of scrolls in engagement.
  • Reciprocating compressors are known in a crank method for compressing a refrigerant by converting a rotational force of a rotary motor into a linear motion, and a vibration method for compressing a refrigerant using a linear motor performing a linear reciprocating motion.
  • a vibration-type reciprocating compressor is called a linear compressor, and such a linear compressor has advantages in that there is no mechanical loss associated with converting a rotary motion into a linear reciprocating motion, thereby improving efficiency and having a simple structure.
  • Patent Document 1 Korean Patent Application No. 10-2018-0065583 (June 6, 2018) discloses a compressor capable of reducing friction loss by reducing a substantial friction area between a cylinder and a piston.
  • the heat emitted to the inside causes the temperature of the suction gas to increase, thereby degrading the performance of the linear compressor.
  • the oil lubricating between the cylinder and the piston which accounts for a large portion of the heat transferred through the discharge cover, and the high-temperature oil cooling the discharge cover are stored inside the shell including heat, and convective heat and A phenomenon in which the suction refrigerant filled in the shell is overheated due to radiant heat occurs, and it is required to develop a structure that can solve this problem.
  • the present invention has been devised to solve the above problems, and an object of the present invention is to lubricate between the cylinder and the piston, which occupies a large portion of the heat transferred through the discharge cover, and high-temperature oil to cool the discharge cover. It is to provide a linear compressor having a structure that is stored in the shell while including this heat, and has a structure that can solve the phenomenon that the suction refrigerant filled in the shell is overheated due to convective heat and radiant heat by these oils.
  • Another object of the present invention is to provide a heat dissipation member at a position where it can contact oil lubricated between the cylinder and the piston inside the shell, which occupies a large portion of the heat transferred through the discharge cover, and high-temperature oil that has cooled the discharge cover.
  • the oil inside the shell can improve heat transfer to the outside.
  • Another object of the present invention is to transfer heat from the high-temperature cylinder of the discharge chamber to the piston so that the intake gas in the piston may be overheated.
  • An object of the present invention is to provide a linear compressor having a structure capable of reducing suction loss by preventing overheating (preheating) of the refrigerant.
  • the linear compressor of the present invention is provided with an oil storage unit for accommodating oil, a shell forming an external appearance; a cylinder installed inside the shell and having an internal space; a piston installed in the cylinder so as to reciprocate in the inner space, and enabling a compression space to be formed in the inner space; and a discharge member provided at one side of the cylinder and having a discharge chamber communicateable with the inner space therein, wherein one side of the shell protrudes so as to allow the internal heat of the shell to be discharged to the outside.
  • a heat dissipation member formed of is installed.
  • the heat dissipation member is disposed inside the shell, a first heat dissipation fin formed to protrude in one direction, is connected to the first heat dissipation fin, and is disposed outside the shell, and a second heat dissipation fin formed to protrude in a direction opposite to the one direction.
  • first heat dissipation fin is formed to protrude in the inner direction of the shell
  • second heat dissipation fin is formed to protrude toward the outside of the shell.
  • the heat dissipation member may further include a fin support portion disposed between the first and second heat dissipation fins in a direction crossing the one direction and supporting the first and second heat dissipation fins.
  • a length of the first heat dissipation fin protruding in one direction may be longer than a length of the second heat dissipation fin protruding in a direction opposite to the one direction.
  • a plurality of first and second heat dissipation fins may be provided, respectively, and an oil flow path for allowing the oil to flow may be provided between the first heat dissipation fins.
  • the first heat dissipation fin extends in a direction crossing the one direction, and an oil suction unit for accommodating oil to be sucked in is provided between one end of the plurality of first heat dissipation fins.
  • the first heat dissipation fins may be disposed in a radial direction.
  • the oil suction part may be provided in a circular or rectangular shape between one end of the plurality of first heat dissipation fins.
  • some of the plurality of first heat dissipation fins are disposed in a radial direction, and another portion of the plurality of first heat dissipation fins crosses the one direction in the radial direction. can be placed as
  • the first heat dissipation fin may have a variable width along the inner direction.
  • An oil passage limiting flow passage through which the flow of the oil is restricted may be provided between the first heat dissipation fins, the ends of which are in contact with the oil flow limiting fins.
  • the heat dissipation member may be coupled to the shell by one of welding, bolting, and press-fitting.
  • An oil supply unit for supplying oil to the cylinder by pumping the oil contained in the oil suction unit to be suckable may be provided inside the shell.
  • the linear compressor of the present invention can communicate with the inside of the oil supply unit to receive the oil from the oil supply unit and supply the supplied oil to the discharge member on one surface of the cylinder. and a frame having an oil supply passage connected thereto and coupled to an outer periphery of the cylinder so as to fix the cylinder, wherein oil passing through the oil supply passage can flow outside the discharge member provided around the discharge chamber .
  • the discharge member may include: an inner discharge cover installed on one side of the cylinder to form the discharge chamber; and a discharge valve disposed in the discharge chamber and opened when the pressure in the compression space is greater than or equal to a predetermined pressure to allow a refrigerant to flow into the discharge chamber, wherein the oil passing through the oil supply passage is disposed around the inner discharge cover. can flow in
  • the heat dissipation member may be coupled through the shell.
  • the linear compressor of the present invention is provided with an oil storage unit for accommodating oil, a shell forming an appearance; a cylinder installed inside the shell and having an internal space; a piston installed in the cylinder so as to reciprocate in the inner space, and enabling a compression space to be formed in the inner space; and a discharge member provided at one side of the cylinder and having a discharge chamber communicateable with the inner space therein, wherein one side of the shell protrudes so as to allow the internal heat of the shell to be discharged to the outside.
  • a heat dissipation member formed of is installed, the oil storage unit is provided at an inner lower portion of the shell, and the heat dissipation member is installed in the oil storage unit.
  • the heat dissipation member includes a first heat dissipation fin disposed inside the shell and formed to protrude in one direction, connected to the first heat dissipation fin, disposed outside the shell, and protruding in a direction opposite to the one direction
  • the second heat dissipation fin may include a formed second heat dissipation fin and a fin support portion disposed between the first and second heat dissipation fins in a direction crossing the one direction and supporting the first and second heat dissipation fins.
  • the heat dissipation member may be coupled through the shell.
  • the oil storage unit may be provided under the shell, and the heat dissipation member may be installed such that at least a portion is submerged in the oil stored in the oil storage unit.
  • An oil suction unit for accommodating oil to be sucked is provided between one end of the first heat dissipation fin, and the oil suction unit is disposed inside the shell to be surrounded by one end of the first heat dissipation fin.
  • An oil supply unit for supplying oil to the cylinder by pumping the oil contained in the oil suction unit to be suckable by having an oil suction pipe is provided, the first heat dissipation fins are provided in plurality, and the plurality of first heat dissipation fins are provided. Between them, an oil flow path for allowing the oil to flow may be provided.
  • the oil storage unit may be provided below the oil supply unit in the interior of the shell.
  • the plurality of first heat dissipation fins are disposed in a radial direction, some of the plurality of first heat dissipation fins are disposed in a radial direction, and another portion of the plurality of first heat dissipation fins is disposed in a radial direction in one direction and They may be arranged in an intersecting direction.
  • the plurality of first heat dissipation fins may be disposed in a radial direction.
  • a guide rib disposed between the plurality of first heat dissipation fins and protruded in a direction parallel to the plurality of first heat dissipation fins to guide the flow of oil may be installed in the fin support part.
  • a plurality of labyrinth ribs protruding from the plurality of first heat dissipation fins in a direction crossing the first heat dissipation fins may be installed in the fin support part.
  • a sealing member may be installed between the shell to which the heat dissipation member is coupled and the heat dissipation member to prevent oil leakage between the shell and the heat dissipation member.
  • an oil storage unit for accommodating oil, the shell forming an exterior; a cylinder installed inside the shell and having an internal space; a piston installed in the cylinder so as to reciprocate in the inner space, and enabling a compression space to be formed in the inner space; and a discharge member having a discharge chamber communicateable with the inner space therein, the discharge member being installed at one side of the cylinder, wherein the discharge member is installed at one side of the cylinder to form the discharge chamber discharge cover; and a discharge valve disposed in the discharge chamber and opened when the pressure of the compression space is greater than or equal to a predetermined pressure to allow a refrigerant to flow into the discharge chamber, and one side of the shell is configured to dissipate heat inside the shell to the outside.
  • a heat dissipation member formed in a protruding structure to enable discharging to the furnace may be installed.
  • the heat dissipation member includes a first heat dissipation fin disposed inside the shell and formed to protrude in one direction, connected to the first heat dissipation fin, disposed outside the shell, and protruding in a direction opposite to the one direction It may include a second heat dissipation fin formed.
  • the heat dissipation member may further include a fin support that is disposed between the first and second heat dissipation fins in a direction crossing the one direction and supports the first and second heat dissipation fins.
  • a plurality of first and second heat dissipation fins may be provided, respectively, and an oil flow path for allowing the oil to flow may be provided between the first heat dissipation fins.
  • the first heat dissipation fins extend in a direction crossing the one direction, and between one end of the plurality of first heat dissipation fins, an oil suction unit for accommodating oil to be sucked is provided, the plurality of first heat dissipation fins It may be arranged in a radial direction.
  • some of the plurality of first heat dissipation fins may be disposed in one radial direction, and another portion of the plurality of first heat dissipation fins may be disposed in a direction crossing the one radial direction.
  • the heat dissipation fin structure increases the contact area between the oil and the shell in the shell to increase the amount of heat dissipation.
  • the linear compressor of the present invention increases the heat transfer area (A) by mounting a heat dissipation member including the first and second heat dissipation fins in the oil storage unit having a high convective heat transfer coefficient (h) compared to the refrigerant, thereby increasing the heat transfer area (A) inside the shell. It is possible to maximize the amount of heat dissipation to the outside.
  • the value of the convective heat transfer coefficient is increased due to the structure of the first heat dissipation fin in the direction toward the oil suction part in order to maximize the oil flow rate.
  • the linear compressor of the present invention is transferred from the inside of the shell to the shell through the first heat dissipation fin, and as the amount of heat emitted from the shell to the outside of the shell increases, the temperature of the shell rises more so that the temperature difference with the outside of the shell rises and the shell
  • the heat transfer area is increased through the external heat dissipation fin, and the amount of convective heat transfer and radiant heat transfer between the shell and external air increases, thereby increasing the amount of heat emitted to the outside of the shell, reducing the suction refrigerant temperature, and increasing the efficiency of the linear compressor.
  • FIG. 1 is a cross-sectional view showing a linear compressor of the present invention.
  • FIG. 2 is an exploded perspective view illustrating the cylinder and the piston in FIG. 1 in an exploded view
  • Figure 3 is a perspective view showing the combination of the cylinder and the piston of Figure 2;
  • Fig. 4 is an enlarged cross-sectional view showing an example in which a heat dissipation member is installed inside the shell of the linear compressor;
  • Fig. 5 is a perspective view showing an example in which a heat dissipation member is provided at the bottom of the shell;
  • FIG. 6 is a plan view of the heat dissipation member.
  • FIG. 7 is a perspective view of a heat dissipation member.
  • FIG. 8 is a perspective view of the heat dissipation member of FIG. 7 viewed from below;
  • Fig. 9 is a plan view showing an example of a heat dissipating member in which an oil suction portion is formed in an elongated rectangle in the reciprocating direction;
  • Fig. 10 is a plan view showing an example of a radiating member having a radial structure
  • Fig. 11 is a plan view showing an example of a heat dissipation member having a labyrinth structure
  • FIG. 12 is a cross-sectional view showing the flow of heat emitted through the heat dissipation member and the flow of heat radiated to the outside of the shell.
  • FIG. 13 is a table showing effects due to a heat dissipation member.
  • a structure applied to one embodiment may be equally applied to another embodiment as long as there is no structural and functional contradiction in the different embodiments.
  • FIG. 1 is a cross-sectional view showing the inside of a linear compressor 100 according to the present embodiment.
  • the linear compressor 100 according to the present embodiment is provided with an oil storage unit 110c for accommodating oil, a shell 110 forming an external appearance, and an interior of the shell 110 .
  • It has a discharge chamber (D) that can communicate with the space, and includes a discharge member 160 installed on one side of the cylinder (120).
  • a heat dissipation member 111 is installed on one side of the shell 110 to have a protruding structure to allow the heat inside the shell 110 to be radiated to the outside.
  • the linear compressor 100 of the present invention has a structure for preventing a decrease in compression efficiency due to overheating of the suction temperature.
  • the linear compressor 100 of the present invention has a structure capable of improving heat transfer to the outside of the shell 110 by using the piston 130 lubricating oil, which occupies a large portion of the heat transferred through the discharge cover. .
  • the shell 110 may be configured by combining the lower shell 110a and the upper shell 110b as shown in FIG. 1 .
  • the shell 110 includes a suction unit 101 through which the refrigerant is introduced and a discharge unit 105 through which the refrigerant compressed in the cylinder 120 is discharged.
  • the discharge unit 105 may be, for example, a pipe that enables the compressed refrigerant to be discharged.
  • the refrigerant sucked through the suction unit 101 moves to the inside of the piston 130 through the suction muffler 150 . Noise may be reduced while the refrigerant passes through the suction muffler 150 .
  • 1, 4 and 5 show an example in which the heat dissipation member 111 is installed in the lower shell 110a.
  • FIG. 6 a plan view of the heat dissipation member 111 is shown in FIG. 6
  • FIGS. 7 and 8 a perspective view of the heat dissipation member 111 is shown in FIGS. 7 and 8 .
  • the heat dissipation member 111 may be installed in the lower shell 110a, and more specifically, may be located in the vicinity of the suction unit 190 side, and more precisely, the suction unit 190. of the oil suction pipe 193 is partially accommodated by the heat dissipation member 111 .
  • the heat dissipation member 111 may be coupled to penetrate the lower shell 110a from the bottom surface of the lower shell 110a, and this structure is shown in FIGS. 1, 4 and 5 .
  • a sealing member is installed to prevent oil from leaking from the bottom surface of the lower shell 110a to the periphery of the heat dissipation member 111 .
  • the heat dissipation member 111 may have a cylindrical shape having a predetermined width as a whole, and is formed to include a protruding structure that enables the heat inside the shell 110 to be discharged to the outside.
  • each of the first and second heat dissipation fins 111a and 111b to be described later is disposed in a radial direction, and the first and second heat dissipation fins 111a and 111b along the circumferential direction are disposed while maintaining a preset interval. can be confirmed through FIG. 6 .
  • the shape of the heat dissipation member 111 is not necessarily limited to such a cylindrical shape structure, and a polygonal shape that enables efficient heat dissipation in consideration of the shape of the shell 110 or configurations around the heat dissipation member 111 . or any other shape.
  • the heat dissipation member 111 may include a first heat dissipation fin 111a and a second heat dissipation fin 111b.
  • the first heat dissipation fin 111a is disposed inside the shell 110 and is formed to protrude in one direction.
  • the second heat dissipation fin 111b is connected to the first heat dissipation fin 111a, is disposed outside the shell 110, and protrudes in a direction opposite to the one direction.
  • the first heat dissipation fin 111a may be formed to be longer than the second heat dissipation fin 111b. it is preferable
  • the linear compressor is installed in the machine room of the refrigerator. , may be formed in the same direction as the first heat dissipation fin.
  • the present invention is not necessarily limited to this structure, and the second heat dissipation fin 111b may be formed in a radial structure as in the arrangement of the first heat dissipation fins 311a and 411b of FIGS. 10 and 11 to be described later.
  • the first heat dissipation fin 111a is formed to protrude inward from the inside of the shell 110
  • the second heat dissipation fin 111b protrudes toward the outside of the shell 110 in FIGS. 7 and FIG. 8 is shown in detail.
  • the first heat dissipation fin 111a has a predetermined width in the circumferential direction in the shell 110, and the first heat dissipation fin 111a protrudes upwardly. has been
  • the second heat dissipation fin 111b has a predetermined width in the circumferential direction, and the second heat dissipation fin 111b is formed to protrude downward. .
  • the heat dissipation member 111 may further include a fin support 114 supporting the first and second heat dissipation fins 111a and 111b.
  • the fin support 114 includes the first and second heat dissipation fins 111a and 111b. ) between the first and second heat dissipation fins 111a and 111b.
  • the fin support 114 having a disk shape of a predetermined width is shown.
  • the first and second heat dissipation fins 111a and 111b) Since it extends to the circumferential surface of the silver disk, it may have a cylindrical shape as a whole.
  • a plurality of first and second heat dissipation fins 111a and 111b may be provided.
  • An oil flow path 111c allowing oil to flow may be provided between the plurality of first heat dissipation fins 111a disposed inside the shell 110 .
  • a plurality of first heat dissipation fins 111a are arranged to be spaced apart in the circumferential direction, and an oil flow path 111c is provided between the first heat dissipation fins 111a.
  • Each oil flow path 111c is formed in a radial direction and provided to communicate with an oil suction part 111d to be described later.
  • FIG. 7 shows an example in which the oil passage 111c is provided between the first heat dissipation fins 111a in the circumferential direction and is formed up to the oil suction part 111d in the radial direction.
  • the oil accommodated in the oil storage unit 110c may be supplied to the oil suction unit 111d through the oil passage 111c.
  • the oil passage restricting flow path in which the flow of the oil is restricted. (111e) is provided.
  • FIGS. 7 and 8 An example in which an oil passage limiting passage 111e in which oil is restricted by an oil flow limiting pin 113 is provided around the oil passage 111c is shown in FIGS. 7 and 8 .
  • an oil supply unit 190 to be described later may be connected to the oil suction unit 111d.
  • the oil storage unit 110c may be provided at an inner lower portion of the shell 110 , and the heat dissipation member 111 may be installed in the oil storage unit 110c.
  • a place where the heat dissipation member 111 is installed in FIG. 5 may be understood as a place where oil is stored inside the shell 110 .
  • the first heat dissipation fins 111a extend in a direction crossing the one direction in which the first heat dissipation fins 111a protrude. In addition, between one end of the plurality of first heat dissipation fins 111a, the plurality of first heat dissipation fins 111a are disposed in a radial direction so that an oil suction unit 111d for accommodating oil to be sucked is provided.
  • the oil accommodated in the oil suction unit 111d is pumped by the oil supply unit 190 to be described later, and the oil is supplied to the cylinder 120 .
  • the oil suction part 111d may be formed in a cylindrical shape having a predetermined volume inside the ends of the plurality of first heat dissipation fins 111a toward the center of the fin support part 114 .
  • the first heat dissipation fins 111a may have different widths along the inner direction.
  • the first heat dissipation fin 111a may have different widths in the central direction of the fin support 114 , and gradually inward toward the center of the fin support 114 .
  • a wide width can be provided.
  • the speed of the oil flowing to the oil suction unit 111d may be improved, which may be understood as a direct oil suction structure.
  • the heat dissipation member 111 may further include an oil flow limiting fin 113 , the oil flow limiting fin 113 being disposed between some of the plurality of first heat dissipating fins 111a and the other to restrict the flow of oil. to limit
  • FIG. 7 and 8 show an example in which four oil flow limiting pins 113 are arranged while maintaining a predetermined angle. Between the four oil flow limiting fins 113, a plurality of first heat dissipation fins 111a are disposed, some of the first heat dissipation fins 111a extend in the front and rear directions based on the drawing, and some of the first heat dissipation fins 111a extend in the left and right directions. The heat dissipation fin 111a is extended.
  • the number of the first heat dissipation fins 111a is not necessarily limited to this number.
  • some of the plurality of first heat dissipation fins 111a are disposed in a radial direction, and other portions of the plurality of first heat dissipation fins 111a are disposed in a direction crossing the radial direction.
  • each of the aforementioned front and rear are arranged in one radial direction (front-rear direction in the drawing), and 9 on the right side and 11 on the left side intersect with one radial direction (left-right direction in the drawing) can be placed as
  • FIGS. 4 and 5 an example in which the second heat dissipation fin 111b is formed to protrude outward from the outside of the shell 110 is shown in FIGS. 4 and 5 .
  • the second heat dissipation fin 111b has a predetermined width in the circumferential direction from the outside of the shell 110, and the second heat dissipation fin 111b is formed to protrude downward. has been
  • a plurality of second heat dissipation fins 111b are arranged to be spaced apart in the circumferential direction, and as described above, an oil flow path 111c is provided between the first heat dissipation fins 111a.
  • Each oil flow path 111c is formed in a radial direction and provided to communicate with an oil suction part 111d to be described later.
  • the oil accommodated in the oil storage unit 110c can be supplied to the oil suction unit 111d through the oil passage 111c, and at this time, the oil flow limiting fin from the first heat dissipation fin 111a Heat may be transferred to the second heat dissipation fin 111b through 113 , and heat is discharged from the second heat dissipation fin 111b to the outside.
  • the oil storage unit 110c may be provided at an inner lower portion of the shell 110 , and the heat dissipation member 111 may be installed in the oil storage unit 110c.
  • a place where the heat dissipation member 111 is installed may be understood as a place where oil is stored inside the lower shell 110b.
  • the second heat dissipation fin 111b extends in a direction crossing the one direction in which the second heat dissipation fin 111b protrudes, similarly to the structure of the first heat dissipation fin 111a.
  • the second heat dissipation fin 111b may also have different widths along the inner direction.
  • the second heat dissipation fin 111b may have different widths in the center direction of the fin support 114 , the fin support 114 . ), it is possible to gradually provide a wider width in the inner direction, which is the center direction.
  • FIG. 7 shows an example in which four oil flow limiting pins 113 are arranged while maintaining a predetermined angle.
  • a plurality of second heat dissipation fins 111b are disposed between the four oil flow limiting plates, and although not clearly shown in the drawing, some of the second heat dissipation fins 111b extend in the front and rear directions based on the drawing, and in the left and right directions Another part of the second heat dissipation fin 111b is extended.
  • the number of the second heat dissipation fins 111b is not necessarily limited to this number.
  • some of the plurality of second heat dissipation fins 111b are disposed in a radial direction, and other portions of the plurality of second heat dissipation fins 111b are disposed in the radial direction. It can be arranged in a direction that intersects with one direction toward the .
  • each of the aforementioned front and rear are arranged in one radial direction (front-rear direction in the drawing), and 9 on the right side and 11 on the left side intersect with one radial direction (left-right direction in the drawing) can be placed as
  • the heat dissipation member 111 may be coupled to the lower shell 110a by one of welding, bolting, and press-fitting.
  • 5 shows an example in which the heat dissipation member 111 is coupled to the bottom surface of the lower shell 110a, and although it is not clearly shown which coupling method it is, it can be understood that it is coupled by one of welding, bolting, and press-fitting. have.
  • the heat dissipation member 111 is coupled to the lower shell 110a by one of welding, bolting and press-fitting, as described above, between a portion of the bottom surface of the lower shell 110a and the heat dissipation member 111 . It is preferable that a sealing member is installed to prevent oil from leaking from the bottom surface of the lower shell 110a to the periphery of the heat dissipation member 111 .
  • FIG. 9 is a plan view showing an example of the heat dissipation member 211 in which the oil suction part 211d is formed in a long rectangular shape in the reciprocating direction.
  • the heat dissipation member 211 of the embodiment shown in FIG. 9 has no difference from the heat dissipation member 111 described above in the description of FIG. 6 in that the arrangement of the first heat dissipation fins 211a is arranged in the vertical and left and right directions. , the oil suction part 111d is formed in a circular structure in FIG. 6, whereas the heat dissipation member 211 in FIG. It is different from the above-described heat dissipation member 111 in that respect.
  • FIG. 10 is a plan view showing an example of the radiation member 311 having a radial structure.
  • the heat dissipation member 311 of the embodiment shown in FIG. 10 is the heat dissipation member ( 111, 211) are different.
  • the oil suction part 311d is formed in a circular structure as shown in FIG. 6 .
  • a guide rib 311e disposed between the plurality of first heat dissipation fins 311a and formed to protrude in a direction parallel to the plurality of first heat dissipation fins 311a to guide the flow of oil. installed to guide the smooth flow of oil.
  • FIG. 11 is a plan view showing an example of the heat dissipation member 411 having a labyrinth structure.
  • the heat dissipation member 411 of the embodiment shown in FIG. 11 is different from the heat dissipation member 311 described above in FIG. There is no difference.
  • the oil suction part 411d has a circular structure as shown in FIGS. 6 and 10 .
  • FIG. 11 an example in which a plurality of labyrinth ribs 411e protruding from the plurality of first heat dissipation fins 411a in a direction intersecting with the first heat dissipation fins 411a are installed in the fin support 414 is shown in FIG. 11 . It allows the oil to stay for a long time to further increase the efficiency of heat transfer.
  • a compression space P in which the refrigerant is compressed by the piston 130 is formed in the cylinder 120 .
  • a suction hole 131b for introducing a refrigerant into the compression space P is formed in the piston 130, and a suction valve 133 for selectively opening the suction hole 131b is provided at one side of the suction hole 131b.
  • the suction valve 133 may be made of a steel plate.
  • a discharge member 160 for discharging the refrigerant compressed in the compression space (P) is provided on one side of the compression space (P). That is, the compression space P may be understood as a space formed between one end of the piston 130 and the discharge member 160 . Also, in the present invention, the discharge member 160 may be understood as a discharge valve assembly, which is a structure including the discharge valve 162 .
  • the discharge member 160 forms a discharge chamber D of the refrigerant, and the inner discharge cover 161 installed on one side of the cylinder 120 and the compression space P are opened when the pressure in the compression space P is equal to or greater than the discharge pressure. and a discharge valve 162 for introducing the refrigerant into the discharge chamber (D).
  • Oil passing through the oil supply passage 173 of the frame 170 to be described later is allowed to flow around the inner discharge cover 161 around the inner discharge cover 161 .
  • an oil groove through which oil can flow may be provided on the outer periphery of the inner discharge cover 161 .
  • the discharge member 160 may further include a valve spring 163 provided between the discharge valve 162 and the inner discharge cover 161 to provide an elastic force in the reciprocating direction of the piston 130 .
  • the reciprocating direction of the piston 130 may be understood as “axial direction”, and may also be understood as the same meaning as moving in the direction in which the piston 130 moves from side to side in FIG. 1 .
  • the suction valve 133 may be formed on one side of the compression space P, and the discharge valve 162 may be provided on the other side of the compression space P, that is, on the opposite side of the suction valve 133 .
  • the inner discharge cover 161 may reduce the flow noise of the compressed refrigerant, and the loop pipe 164 guides the compressed refrigerant to the discharge unit 105 .
  • the roof pipe 164 is coupled to the inner discharge cover 161 to extend curvedly, and is coupled to the discharge unit 105 .
  • heat generated in the discharge chamber D during compression through the discharge unit 105 may be discharged to the outside of the shell 110 .
  • the discharge member 160 may further include an outer discharge cover 165 coupled to the inner discharge cover 161 .
  • the roof pipe 164 may be coupled to the outer discharge cover 165 spaced apart from the inner discharge cover 161 by a predetermined distance.
  • the linear compressor 100 of the present invention may further include a frame 170 .
  • the frame 170 is a member for fixing the cylinder 120 , and may be configured integrally with the cylinder 120 or may be fastened by a separate fastening member.
  • the inner discharge cover 161 may be coupled to the frame 170 .
  • the frame 170 includes an oil supply flow path 173 , the oil supply flow path 173 can communicate with the interior of the oil supply unit 190 to receive the oil from the oil supply unit 190 and receive the supplied oil. It is connected to one surface of the cylinder 120 so that oil can be supplied to the discharge member 160 .
  • the oil supply flow path 173 is formed from the lower side of the shell 110 to the upper left direction on a cross-sectional basis, but is not necessarily limited to this direction.
  • Oil passes through the oil supply passage 173 and can flow from the outside of the discharge member 160 provided around the discharge chamber D.
  • a flow path formed to pass oil to enable heat dissipation and to be supplied back to the oil storage unit 110c may be provided on the outer periphery of the discharge member 160 .
  • the heat of the discharge chamber (D) generated by the compression of the piston 130 is discharged to the outside of the shell 110 through the above-described discharge portion 105 or a frame adjacent to the discharge chamber (D) Heat transfer is made through 170 and the cylinder 120 .
  • a heat transfer system inside and outside the shell 110 through oil in the linear compressor 100 of the present invention will be described.
  • the oil accommodated in the oil storage unit is pumped through the oil supply unit 190, and is provided to the end of the cylinder 120 through the oil supply passage 173 of the frame 170. .
  • oil flows into the discharge member 160 , and as shown in FIG. 1 , the oil introduced into the discharge member 160 is a discharge member provided around the discharge chamber (D). (160) will flow on the outer periphery.
  • the oil flowing from the outer periphery of the discharge member 160 is laminated on the oil storage unit 110c of the shell 110 .
  • the oil receives heat from the discharge chamber D in the discharge member 160 , and the heated oil is stacked on the oil storage unit 110c, and the first and second heat dissipation fins 111a of the heat dissipation member 111 are heated. , 111b) through the heat is emitted to the bottom of the shell 110.
  • heat is emitted to the outside of the shell 110 or oil flowing around the discharge member 160 is stored in the oil storage unit 110c, and the heat dissipation member 111 .
  • the heat dissipation member 111 including the first and second heat dissipation fins 111a and 111b in the oil storage unit 110c having a convective heat transfer coefficient (h) higher than that of the refrigerant. ) to increase the heat transfer area (A) to maximize the amount of heat dissipation from the inside of the shell 110 to the outside of the shell 110 .
  • Equation 1 Q cov is the amount of heat transferred due to conduction, h is the convective heat transfer coefficient, A is the heat transfer area, and ⁇ T is the temperature difference.
  • Equation 2 is a more concrete expression of [Equation 1].
  • Equation 2 Q cov is the amount of heat transferred due to conduction, h is the convective heat transfer coefficient, A s is the heat transfer area through which heat is conducted in the shell 110, T s - T ⁇ is the outside temperature and the shell 110 ) represents the difference between the temperatures.
  • the thermal conductivity coefficient of refrigerant is 0.0177 W/m-K (at 0.559 bar pressure and 32.2 °C temperature), and the thermal conductivity coefficient of oil is 0.18 W/m-K (based on 40 °C temperature) to be.
  • Equation 3 Q rad is the amount of heat transferred due to radiation, ⁇ is the radiative heat transfer coefficient, A is the heat transfer area, and T s -T ⁇ is the difference between the outside air temperature and the temperature of the shell 110 .
  • Equation 4 Q rad is the amount of heat transferred due to radiation, ⁇ is the Stefan Boltzmann constant 5.6703 * 10 -8 [W/(m2 * K4)], ⁇ s is the radiative heat transfer coefficient, A s is the shell (110 ), the heat transfer area through which heat is conducted, T ⁇ is the outside air temperature, and T s represents the temperature of the shell 110 .
  • linear compressor 100 of the present invention may further include a motor unit 140 .
  • the motor unit 140 applies a driving force to the piston 130 .
  • the motor unit 140 includes an outer stator 141 fixed to the frame 170 and disposed to surround the cylinder 120 , an inner stator 142 spaced apart from the inner side of the outer stator 141 , and the outer and a magnet 143 positioned in a space between the stator 141 and the inner stator 142 .
  • the magnet 143 is made of a permanent magnet and can reciprocate linearly by mutual electromagnetic force between the outer stator 141 and the inner stator 142 . And, the magnet 143 may be composed of a single magnet having one pole, or a plurality of magnets having three poles are combined.
  • the magnet 143 may be coupled to the piston 130 by the connecting member 144 .
  • the connecting member 144 may extend from one end of the piston 130 to the magnet 143 . Accordingly, as the magnet 143 moves linearly, the piston 130 may linearly reciprocate in the axial direction together with the magnet 143 .
  • the outer stator 141 includes a stator core 141a and a coil winding body 145 .
  • a plurality of laminations are stacked in the stator core 141a in a circumferential direction, and the stator core 141a may be disposed to surround the coil winding body 145 .
  • the magnetic flux flowing along the outer stator 141 and the inner stator 142 and the magnetic flux of the magnet 143 interact to generate a force to move the magnet 143 .
  • a stator cover 146 is provided on one side of the outer stator 141 .
  • One end of the outer stator 141 may be supported by the frame 170 , and the other end may be supported by the stator cover 146 .
  • the inner stator 142 is fixed to the outer periphery of the cylinder 120 .
  • a plurality of stator cores are radially stacked on the outer circumferential surface of the cylinder 120 in the circumferential direction.
  • the linear compressor 100 further includes a supporter 181 for supporting the piston 130 and a back cover 182 extending from the piston 130 toward the suction unit 101 .
  • the back cover 1182 may be disposed to cover at least a portion of the suction muffler 150 .
  • the linear compressor 100 includes a plurality of springs 183a and 183b so that the piston 130 can resonate.
  • the spring consists of a compression coil spring provided in the axial direction.
  • the plurality of springs 183a and 183b includes a first spring 183a supported between the supporter 181 and the stator cover 146 and a second spring supported between the supporter 181 and the back cover 182 ( 183b).
  • the elastic modulus of the first spring 183a and the second spring 183b may be the same.
  • a position where the first spring 183a is installed may be defined as a “front” and a position where the second spring 183b is installed may be defined as a rearward.
  • the front may be defined in a direction toward the compression space P or in a direction from the piston 130 toward the suction unit, and the rear as a direction away from the compression space P or in a direction from the suction unit toward the discharge member 160.
  • a predetermined oil may be stored on the inner bottom surface of the shell 110 .
  • a portion in which oil is stored on the inner bottom surface of the shell 110 may be referred to as an oil storage unit 110c.
  • the oil storage unit 110c may be provided as a separate space enabling storage of oil on the bottom surface of the shell 110 , or may simply be accommodated on the inner bottom surface of the shell 110 without a separate space.
  • an oil supply unit 190 for pumping oil may be provided at a lower portion of the shell 110 .
  • the oil supply unit 190 makes it possible to supply oil to the cylinder 120 by pumping the oil accommodated in the oil suction part 111d of the above-described heat dissipation member 111 to be suctionable.
  • the oil supply unit 190 may be operated by vibration generated as the piston 130 reciprocates linear motion to pump oil upward. Accordingly, the oil pumped from the oil supply unit 190 is supplied to the space between the cylinder 120 and the piston 130, and performs a series of cooling and lubrication actions.
  • the cylinder 120 is provided with an oil supply hole (128).
  • the oil supplied between the inner circumferential surface of the cylinder 120 and the outer circumferential surface of the piston 130 through the oil supply unit 190 lubricates between the inner circumferential surface of the cylinder 120 and the outer circumferential surface of the piston 130 .
  • the friction loss between the cylinder 120 and the piston 130 still occurs.
  • This embodiment minimizes the friction area between the cylinder 120 and the piston 130 while maintaining the concentricity of the cylinder 120 and the piston 130 to reduce the friction loss between the cylinder 120 and the piston 130. is to make it
  • FIG. 2 is an exploded perspective view showing the cylinder 120 and the piston 130 according to FIG. 1
  • FIG. 3 is a perspective view showing the cylinder 120 and the piston 130 assembled in FIG. 2 .
  • the piston 130 has a substantially cylindrical shape and extends in the axial direction in the piston 130 body 131 and the piston 130 in the radial direction from the rear end of the body 131 .
  • the piston 130 extending to the flange 132 is included.
  • the piston 130 body 131 includes a front portion 131a forming the front end of the piston 130 body 131 .
  • a suction valve 133 is installed on the front part 131a. Accordingly, the refrigerant flowing in the piston 130 body 131 may be sucked into the compression space P through the suction hole 131b.
  • the piston 130 body 131 further includes an inclined portion 131c extending obliquely backward from the front portion 131a.
  • the inclined portion 131c may extend in a direction in which the outer diameter of the main body 131 of the piston 130 is greater than the outer diameter of the front portion 131a. Accordingly, the piston 130 main body 131 may be inclined so that the outer diameter increases from the front part 131a to the rear by the inclined part 131c. Accordingly, when the piston 130 moves forward, a portion of the refrigerant in the compression space P moves to the front-end space formed between the inclined portion 131c and the inner circumferential surface of the cylinder 120 . Then, the refrigerant that has moved to the front-end space is gradually compressed so that the front-end of the piston 130 can be suppressed from contacting the inner circumferential surface of the cylinder 120 .
  • the piston 130 main body 131 is a bearing portion on the side of the first piston 130 in a direction away from the compression space P based on the compression space P (hereinafter, the first piston portion 135). 135 and the second piston 130-side bearing portion (hereinafter, the second piston portion 136) 136 are formed to be spaced apart by a predetermined interval.
  • the piston 130 side avoiding part ( Hereinafter, a first avoidance portion) 137 is formed. 2 to 4 , the piston 130 side avoidance portion may be formed between the second piston portion 136 and the piston 130 flange 132 .
  • the outer diameter of the first piston part 135 and the outer diameter of the second piston part 136 are formed equal to each other, or the outer diameter of the first piston part 135 is slightly larger than the outer diameter of the second piston part 136.
  • the first piston unit 135 may function as a main bearing
  • the second piston unit 136 may function as a sub bearing. This is to minimize leakage of the refrigerant compressed in the compression space P between the cylinder 120 and the piston 130 as the compression space P is formed on the front side of the first piston part 135 . .
  • the reciprocating length (or axial length) of the first piston part 135 is greater than the reciprocating length of the first cylinder 120-side bearing part to be described later, and the reciprocating length of the first cylinder 120-side bearing part and the cylinder (120) It may be formed smaller than the total length of the second sum of the reciprocating length of the side avoidance portion. This will be explained again later.
  • a surface where the first piston part 135 and the first avoiding part 137 meet or a surface where the first avoiding part 137 and the second piston part 136 meet may be formed as inclined surfaces 137a, respectively. Accordingly, the oil accumulated in the first avoidance part 137 may be smoothly introduced into each bearing surface along each inclined surface 137a during the reciprocating linear motion of the piston 130 .
  • the cylinder 120 is formed in a substantially cylindrical shape like the piston (130).
  • the cylinder 120 has an inner diameter larger than the outer diameter of the piston 130 body 131 by several ⁇ m. Accordingly, the inner circumferential surface of the cylinder 120 and the outer circumferential surface of the piston 130 main body 131 are almost in contact or correspond to each other with a fine lubricating film therebetween.
  • the inner circumferential surface of the cylinder 120 has the first cylinder 120 side bearing part (hereinafter, the first cylinder part) 125 and the second cylinder ( 120) side bearing parts (hereinafter, second cylinder parts) 126 are formed at regular intervals.
  • a second avoidance portion 127 is formed to extend between the first cylinder portion 125 and the second cylinder portion 126 .
  • the inner diameters of the first cylinder part 125 and the second cylinder part 126 are formed to be substantially the same.
  • the first cylinder part 125 includes the first piston part 135
  • the second cylinder part 126 includes the second piston part 136
  • the second avoidance part 127 includes the first avoidance part 137 and Each is formed to overlap at least a part.
  • the reciprocating length of the first cylinder part 125 may be at least equal to or longer than the maximum moving distance of the piston 130 .
  • the reciprocating length (A) of the first cylinder part 125 is formed to be larger than the maximum moving distance.
  • the maximum moving distance of the piston 130 is the distance that the front part 131a of the piston 130 can move the furthest from the discharge valve 162, which can be defined as a state in which the second spring 183b is fully pressed. have.
  • the reciprocating length of the first piston part 135 is formed to be larger than the reciprocating length of the second avoiding part 127
  • the reciprocating direction length of the first avoiding part 137 is that of the first cylinder part 125 . It may be formed to be larger than the reciprocating direction length. Accordingly, even if the piston 130 moves as much as the maximum movement distance, the first piston part 135 does not catch or fall off the second avoidance part 127 , so that the piston 130 smoothly reciprocates in the cylinder 120 . You can exercise.
  • the reciprocating length of the first piston part 135 is too long, when the piston 130 moves by the maximum moving distance, the first piston part 135 moves to the first cylinder part 125 as well as the second cylinder part ( 126) can also be used. Then, as a whole, the contact area between the cylinder 120 and the piston 130 increases to increase the friction area as well as the rear end of the first piston part 135 to the front end of the second cylinder part 126 .
  • the reciprocating linear motion of the piston 130 may be obstructed by being caught. Therefore, it is preferable that the reciprocating length of the first piston part 135 is smaller than the second total length of the first cylinder part 125 in the reciprocating direction and the reciprocating length of the second avoiding part 127 .
  • the sum of the reciprocating length of the first piston part 135 and the maximum moving distance of the piston 130 is the reciprocating length of the first cylinder part 125 and the reciprocating length of the second avoiding part 127 . It is preferable to be formed smaller than the sum of the second total length.
  • the first avoidance part 137 is covered by the second cylinder part 126 so that the oil is transferred to the first It may be prevented from flowing into the avoidance part 137 . Then, the oil may be blocked from being supplied between the second cylinder part 126 and the second piston part 136 . Therefore, the reciprocating length of the first piston part 135 is longer than the length of the first cylinder part 125 as defined above, but even when the piston 130 moves by the maximum moving distance, the second avoidance part 127 . and the first avoiding portion 137 may overlap the length, ie, it is preferable to form such that it does not exceed the second avoiding portion 127 .
  • first cylinder part 125, the second avoidance part 127, and the second cylinder part 126 are sequentially formed on the inner peripheral surface of the cylinder 120, and the second cylinder part 125 is formed on the inner peripheral surface of the piston 130 corresponding thereto.
  • the first piston part 135 , the first avoiding part 137 , and the second piston part 136 may be sequentially formed.
  • the first piston part 135 is the first cylinder part 125 and the second piston part 136 is the second cylinder part ( 126) and each bearing contact.
  • the piston 130 moves forward, the piston 130 moves toward the discharge valve 162 while compressing the refrigerant in the compression space P.
  • the first piston part 135 moves toward the discharge valve 162 while compressing the refrigerant in the compression space P.
  • the first piston part 135 in a state in which the first piston part 135 is in bearing contact with the first cylinder part 125 , the front side of the first piston part 135 is within the range of the first cylinder part 125 , the first piston part 135 .
  • the first piston part 135 is outside the range of the first cylinder 125 by a predetermined interval. This is because the reciprocating length of the first piston part 135 is longer than the reciprocating length of the first cylinder part 125 .
  • the piston 130 does not sag in the radial direction as the first piston unit 135 is supported by the first cylinder unit 125 .
  • the second piston unit 136 is in bearing contact with the second cylinder unit 126 , so that the piston 130 can be supported more stably.
  • the first avoiding part 137 is formed on the outer peripheral surface of the piston 130 and the second avoiding part 127 is formed on the inner peripheral surface of the cylinder 120 , respectively, and the first avoiding part 137 is the cylinder 120 . ), and the second avoidance portion 127 does not come into contact with the piston 130 . Accordingly, the frictional area between the cylinder 120 and the piston 130 is reduced as a whole, thereby reducing the frictional loss.
  • the contact area between the first piston part 135 and the first cylinder part 125 increases when the piston 130 performs a compression stroke.
  • the pressure of the compression space P increases during the compression stroke, it may be advantageous in terms of sealing to increase the contact area between the first piston part 135 and the first cylinder part 125 .
  • the contact area between the first piston part 135 and the first cylinder part 125 is reduced.
  • the pressure in the compression space P is reduced when the suction stroke is performed, the compressor efficiency is not greatly affected.
  • the bearing contact length between the cylinder 120 and the piston 130 is the same regardless of the movement distance of the piston 130, but in this embodiment, the cylinder 120 and the piston ( 130), the contact length of the bearings decreases linearly. Then, since the average friction length per cycle of the piston 130 is reduced, the friction loss between the cylinder 120 and the piston 130 is reduced, so that the compressor efficiency can be improved. In addition, through this, it is possible to suppress damage to the cylinder 120 and the piston 130 while facilitating the manufacture of the cylinder 120 or the piston 130 .
  • the piston 130 is supported in a cantilever shape by a plurality of springs 183a and 183b made of compression coil springs, if the support area for the piston 130 is small, the piston 130 is Deflection may occur depending on its own weight.
  • the first piston part 135 and the second piston part 136 are arranged in the axial direction, and these piston 130 side bearing parts 135 and 136 are respectively connected to the first cylinder part 125 and As it is radially supported by the second cylinder part 126 , it is possible to stably support the sagging of the piston 130 .
  • first piston part 135 and the second piston part 136 in the piston 130 are spaced apart by the reciprocating length of the first avoiding part along the axial direction, but the piston At 130, only one piston 130-side bearing portion is formed.
  • the inner circumferential surface of the cylinder 120 is the same as in the above-described embodiment. That is, the first cylinder portion 125 and the second cylinder portion 126 are formed on the inner circumferential surface of the cylinder 120 with the second avoidance portion 127 interposed therebetween.
  • the inner diameter of the first cylinder part 125 and the inner diameter of the second cylinder part 126 are formed to be the same, and the inner diameter of the second avoidance part 127 is formed to be larger than the inner diameter of both cylinder parts 125 and 126 .
  • the second avoiding portion 127 is formed to be recessed by a predetermined depth from the inner circumferential surface of the cylinder 120 toward the outer circumferential surface.
  • the piston 130 side bearing part 135 is formed on the outer peripheral surface of the piston 130 body 131 on the front side, and the piston 130 side bearing part 135 is formed on the rear end of the piston 130 side bearing part 135 .
  • the piston 130 side avoidance portion 137 having an outer diameter smaller than the outer diameter of the portion 135 is formed.
  • the piston 130 flange 132 described above is formed. Accordingly, one piston 130-side bearing portion corresponding to the aforementioned first piston 130-side bearing portion is formed in the piston 130 body 131 according to the present embodiment.
  • the basic configuration of the cylinder 120 and the piston 130 according to the present embodiment as described above is substantially the same as that of the above-described embodiment.
  • the piston 130 side bearing part 135 is formed only at the front end of the piston 130 body 131, the cylinder 120 and the piston 130 compared to the above-described embodiment.
  • the friction area between them can be further reduced. Through this, the friction loss between the cylinder 120 and the piston 130 can be further reduced.
  • compressor efficiency may be improved.
  • a plurality of springs are provided on the rear side of the piston 130 to induce a resonant motion of the piston 130, but the spring is not necessarily required.
  • the piston 130 may resonate by using the thrust and return force of the magnet except for the spring.
  • FIG. 13 is a table showing the improvement effect according to the reference condition of the suction port temperature, the energy efficiency ratio (EER) improvement, and the refrigerator shutdown. As shown in FIG. 13 , the suction port temperature was decreased by 1.5°C, the EER was increased by 0.06, and 0.6% was improved in relation to the refrigerator burnout.
  • EER energy efficiency ratio
  • the heat dissipating member 111 of the shell 110 is increased, making it possible to reduce the suction refrigerant temperature.
  • the first and second heat dissipation fins 111a and 111b are installed in the oil storage unit 110c in which the oil is accommodated to increase the heat transfer coefficient and heat dissipation surface area. , the heat dissipation effect can be maximized.
  • linear compressor 100 is not limited to the configuration and method of the embodiments described above, and embodiments may be configured by selectively combining all or part of each embodiment so that various modifications can be made.
  • the present invention can be used in a linear compressor having a structure for preventing a decrease in compression efficiency due to overheating of the suction temperature.

Landscapes

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

Abstract

L'invention concerne un compresseur linéaire comprenant : une coque comportant une unité de stockage d'huile permettant de loger de l'huile, et formant l'extérieur ; un cylindre installé à l'intérieur de la coque, et comportant un espace interne ; un piston installé dans le cylindre de façon à effectuer un mouvement alternatif dans l'espace interne, et permettant la formation d'un espace de compression dans l'espace interne ; et un élément d'évacuation comportant une chambre d'évacuation pouvant être en communication avec l'espace interne, et installé sur un côté du cylindre. Un élément de dissipation de la chaleur, prenant la forme d'une structure saillante, est installé sur un côté de la coque afin de permettre la dissipation vers l'extérieur de la chaleur à l'intérieur de la coque.
PCT/KR2022/000890 2021-02-15 2022-01-18 Compresseur linéaire WO2022173138A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020210019974A KR102494485B1 (ko) 2021-02-15 2021-02-15 리니어 압축기
KR10-2021-0019974 2021-02-15

Publications (1)

Publication Number Publication Date
WO2022173138A1 true WO2022173138A1 (fr) 2022-08-18

Family

ID=82837732

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2022/000890 WO2022173138A1 (fr) 2021-02-15 2022-01-18 Compresseur linéaire

Country Status (2)

Country Link
KR (1) KR102494485B1 (fr)
WO (1) WO2022173138A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20050015685A (ko) * 2003-08-07 2005-02-21 엘지전자 주식회사 리니어 압축기의 냉각 구조
KR20050121053A (ko) * 2004-06-21 2005-12-26 삼성전자주식회사 압축기
KR20060081482A (ko) * 2005-01-07 2006-07-13 엘지전자 주식회사 리니어 압축기
JP2008240574A (ja) * 2007-03-26 2008-10-09 Jtekt Corp 遠心圧縮機
KR20190040429A (ko) * 2017-10-10 2019-04-18 엘지전자 주식회사 리니어 압축기

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100613516B1 (ko) * 2004-11-03 2006-08-17 엘지전자 주식회사 리니어 압축기
KR20180065583A (ko) 2016-12-08 2018-06-18 지아동 린 높은 연성 및 솔더링 플럭스를 가진 납-무함유 솔더 조성물을 함유하는 솔더 페이스트

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20050015685A (ko) * 2003-08-07 2005-02-21 엘지전자 주식회사 리니어 압축기의 냉각 구조
KR20050121053A (ko) * 2004-06-21 2005-12-26 삼성전자주식회사 압축기
KR20060081482A (ko) * 2005-01-07 2006-07-13 엘지전자 주식회사 리니어 압축기
JP2008240574A (ja) * 2007-03-26 2008-10-09 Jtekt Corp 遠心圧縮機
KR20190040429A (ko) * 2017-10-10 2019-04-18 엘지전자 주식회사 리니어 압축기

Also Published As

Publication number Publication date
KR20220116743A (ko) 2022-08-23
KR102494485B1 (ko) 2023-02-06

Similar Documents

Publication Publication Date Title
WO2018147574A1 (fr) Compresseur linéaire
WO2017018578A1 (fr) Moteur électrique et son procédé de fabrication
WO2016024691A1 (fr) Aspirateur
WO2013047975A1 (fr) Appareil d'éclairage à base de semi-conducteurs optiques
WO2016195148A1 (fr) Carter pour moteur électrique et son procédé de fabrication, moteur électrique doté d'un carter pour moteur électrique
WO2018143699A1 (fr) Armoire de refroidissement et de chauffage
WO2019221417A1 (fr) Turbocompresseur
WO2019031887A1 (fr) Appareil de traitement de linge et son procédé de commande
WO2021194113A1 (fr) Moteur rotatif
WO2019031885A1 (fr) Appareil de traitement du linge et procédé de commande d'un tel appareil de traitement du linge
WO2019059650A1 (fr) Réfrigérateur
EP3738193A1 (fr) Moteur à aimant permanent intérieur
WO2016098977A1 (fr) Machine électrique rotative
WO2010062131A2 (fr) Moteur thermique
WO2018070618A1 (fr) Dispositif de refroidissement pour caméra de surveillance
WO2019031886A1 (fr) Appareil de traitement de linge et son procédé de commande
WO2009136726A2 (fr) Système d’échange de chaleur
WO2022173138A1 (fr) Compresseur linéaire
WO2020059909A1 (fr) Moteur électrique et module de production d'énergie intelligent le comprenant
WO2019164303A1 (fr) Moteur linéaire et compresseur linéaire le comprenant
WO2022145805A1 (fr) Compresseur linéaire
WO2022149671A1 (fr) Compresseur linéaire
WO2019059651A1 (fr) Réfrigérateur
WO2018135746A1 (fr) Dispositif de commande et procédé de commande pour compresseur linéaire
WO2022149670A1 (fr) Compresseur linéaire

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22752898

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 22752898

Country of ref document: EP

Kind code of ref document: A1