Compressor

Abstract

A reciprocating compressor is disclosed. The reciprocating compressor may comprise: a shell; a compression part; a discharge pipe; a loop pipe; and a damper member, wherein the damper member may be formed of a material having a rigidity that is less than that of the loop pipe to surround at least a portion of the loop pipe. Accordingly, when the compressor is operated to vibrate the loop pipe, a damper member surrounding the loop pipe is deformed by the vibration of the loop pipe so as to absorb and thus reduce the vibration of the loop pipe.

Description

compressor

[0001] The present invention relates to a compressor.

[0002] Compressors can be classified into various types, such as rotary compressors, scroll compressors, and reciprocating compressors, depending on the compression method and the type of refrigerant used. In addition, compressors can be classified into direct discharge methods and indirect discharge methods depending on the refrigerant discharge method. In the former case, the refrigerant discharged from the compression chamber is directly connected to a discharge pipe and discharged, whereas in the latter case, the refrigerant discharged to the compression chamber is discharged through the internal space of the shell and then through a discharge pipe. The present invention relates to the former, i.e., the direct discharge method.

[0003] The direct-discharge compressor described above has a loop pipe installed between the compression chamber and / or the discharge muffler and the discharge pipe to dampen vibrations generated during discharge. Below, a direct-discharge compressor will be described using a reciprocating compressor as an example.

[0004] Reciprocating compressors can be categorized into vibrating and coupled types based on the piston actuation method. In an oscillating reciprocating compressor, the piston is connected to the actuator of a reciprocating motor and vibrates, reciprocating within a cylinder to compress the refrigerant. In a coupled reciprocating compressor, the piston is connected to the shaft of a rotary motor and reciprocates within a cylinder to compress the refrigerant. Hereinafter, reciprocating compressors will be defined as coupled reciprocating compressors.

[0005] These reciprocating compressors are structured so that the compression unit, which compresses the refrigerant, and the electric motor, which provides driving force to the compression unit, are housed within a sealed shell. A discharge pipe is connected through the shell, and the refrigerant compressed in the compression unit is guided to the discharge pipe via the loop pipe described above and discharged to the outside.

[0006] In these reciprocating compressors, vibration generated during the operation of the compression unit can be transmitted to the outside world through the loop pipe. Therefore, minimizing vibration transmitted through the loop pipe is crucial. In particular, as the maximum operating speed of compressors has increased in recent years, the loop pipe has been designed with high rigidity to avoid resonant modes, exacerbating vibration.

[0007] To solve this problem, a method is disclosed in which a coil spring formed of metal, for example, steel, is wound around the outer surface of a loop pipe to absorb vibration of the loop pipe by utilizing friction between the loop pipe and the spring.

[0008] While utilizing steel springs can be effective in reducing vibration at resonance, the steel-to-steel contact between the loop pipe and the steel springs causes additional vibration in the high-frequency range. Furthermore, while longer springs are more effective in reducing vibration, the increased weight lowers the resonance point, limiting the ability to increase spring length.

[0009] In addition, for example, as in Patent Document 1 (Publication No. 10-2005-0071259), a method of forming a loop pipe with a non-metallic material having lower rigidity than steel, such as a plastic material, is disclosed.

[0010] When a loop pipe is manufactured from a non-metallic material, there is an advantage of low vibration transmission due to the nature of the material, but since the loop pipe made of a non-metallic material must be joined to a discharge pipe made of a metal material, there is a problem that it is difficult to ensure airtightness at the joint and fluid leakage may occur.

[0011] Meanwhile, Patent Document 2 (Chinese Patent Publication No. 115523119) discloses a method for reducing vibration by covering a rubber vibration-reducing sleeve with a bent portion of an internal exhaust pipe of a gas compressor and supporting the rubber vibration-reducing sleeve using a plurality of springs and fixed sheets.

[0012] The vibration reduction structure disclosed in Patent Document 2 has the problem that it requires combining multiple members into a complex structure, which makes assembly work cumbersome and increases production costs.

[0013] An object of the present invention is to provide a compressor capable of reducing vibration of a loop pipe not only in the operating range of the compressor but also in the entire vibration frequency band.

[0014] Another object of the present invention is to provide a compressor having a simple structure and capable of effectively reducing vibration of a loop pipe.

[0015] Another object of the present invention is to provide a compressor capable of reducing vibration of a loop pipe at low cost.

[0016] In order to achieve the object of the present invention, a compressor including a shell, a compression unit, a discharge pipe, a loop pipe, and a damper member can be provided. The compression unit is provided in an internal space of the shell and can compress a refrigerant. The discharge pipe can be provided to penetrate the shell. The loop pipe can guide the refrigerant compressed in the compression unit to the discharge pipe. The damper member can wrap a portion of the loop pipe. The damper member can be formed of a material having a stiffness lower than that of the loop pipe. Accordingly, when the compressor operates and the loop pipe vibrates, the damper member wrapping the loop pipe is deformed by the vibration of the loop pipe, thereby absorbing and reducing the vibration of the loop pipe.

[0017] For example, the damper member may be formed of an elastic material. This increases the deformation of the damper member, thereby improving the vibration reduction effect.

[0018] For example, the damper member may be formed with an inner diameter larger than the outer diameter of the loop pipe. Accordingly, the damper member vibrates around the loop pipe, thereby further enhancing the vibration reduction effect.

[0019] As another example, if the damper member is formed of an elastic material and its inner diameter is formed larger than the outer diameter of the loop pipe, a better vibration reduction effect can be obtained.

[0020] For example, the damper member may have at least one damping protrusion formed on its inner surface. Preferably, a plurality of damping protrusions are formed along the inner surface of the damper member, and the minimum diameter of an imaginary circle connecting the plurality of damping protrusions may be formed to be greater than or equal to the outer diameter of the loop pipe.

[0021] The above damping protrusions can reduce vibrations of the loop pipe in various directions by irregularly changing the vibration direction of the damper member. In addition, when oil for lubrication is stored in the internal space of the shell, the oil can be accommodated in the space between the damping protrusions, and the vibration reduction effect of the damper member can be enhanced due to the viscosity of the oil.

[0022] For example, the damper member may be formed in a tube shape, a coil shape, or a plurality of ring shapes.

[0023] If the above damper member is formed in a tube shape, the vibration reduction means can be formed with a very simple structure. Alternatively, if the damper member is formed in a coil shape or a plurality of ring shapes, the damper member can expand and contract in the longitudinal direction of the loop pipe, and thus, vibration in a direction parallel to the longitudinal direction of the loop pipe as well as vibration in a direction orthogonal to the longitudinal direction of the loop pipe can be reduced simultaneously.

[0024] For example, the damper member may include a first damping portion that surrounds the loop pipe and a second damping portion that surrounds the first damping portion. Preferably, the second damping portion may be formed of a material heavier than the first damping portion. Also, preferably, the thickness of the first damping portion may be formed to be greater than or equal to the thickness of the second damping portion.

[0025] Accordingly, the overall weight of the damping member is increased, thereby obtaining a sufficient vibration reduction effect without significantly increasing the size of the damping member, and minimizing interference with other parts in the narrow space of the reciprocating compressor.

[0026] For example, the loop pipe may include a straight portion and a curved portion, and the damper member may be inserted into at least one of the straight portion and the curved portion of the loop pipe.

[0027] When the above damper member is inserted into the straight portion of the loop pipe, vibration in a plane perpendicular to the longitudinal direction of the loop pipe, i.e., two-way vibration, can be reduced, and when the above damper member is inserted into the curved portion of the loop pipe, the vibration reduction effect is reduced, but there is an effect of reducing three-way vibration of the loop pipe.

[0028] For example, the loop pipe may be provided with a stopper to restrict movement of the damper member in the longitudinal direction of the loop pipe. This prevents, particularly when the damper member is installed in a straight portion of the loop pipe, the damper member from moving to a curved portion of the loop pipe, thereby reducing the vibration amplitude of the damper member and reducing the vibration reduction effect.

[0029] For example, a predetermined amount of oil may be stored in the internal space of the shell, and the damper member may be provided so that at least a portion of the oil is immersed in the oil. In this case, the viscosity of the oil, together with the damper member, may reduce vibration of the loop pipe.

[0030] A compressor according to the present invention comprises a damper member that surrounds at least a portion of a loop pipe, wherein the damper member may be formed of a material having a stiffness lower than that of the loop pipe. This allows for an excellent vibration reduction effect not only in the compressor's operating range but also across the entire vibration frequency range.

[0031] The compressor according to the present invention can effectively reduce vibration of a loop pipe with a very simple structure, since the damper member can be formed in the shape of a smooth pipe with a circular or oval inner surface.

[0032] The compressor according to the present invention can reduce vibration of a loop pipe at low cost by using a damper member in the form of a smooth tube made of an elastic member such as rubber.

[0033] Fig. 1 is a perspective view showing the inside of the upper shell of a reciprocating compressor according to the present embodiment.

[0034] Fig. 2 is a cross-sectional view showing the inside of the reciprocating compressor of Fig. 1.

[0035] Fig. 3 is a perspective view showing the installation state of a damper member according to the present embodiment.

[0036] Figure 4 is a cross-sectional view taken along line “Ⅸ-Ⅸ” of Figure 3.

[0037] Fig. 5 is a schematic diagram showing an example in which a damper member is provided on the first straight portion of a loop pipe.

[0038] FIG. 6 and FIG. 7 are graphs comparing the vibration reduction effect of a reciprocating compressor equipped with a damper member according to the present invention with a case without a conventional damper member and a case equipped with a damper member made of a steel spring, respectively. FIG. 6 is a graph comparing vibration in the operating range of a reciprocating compressor, and FIG. 7 is a graph comparing vibration in the full range.

[0039] Fig. 8 is a cross-sectional view showing another embodiment of a damper member.

[0040] Fig. 9 is a cross-sectional view showing another embodiment of a damper member.

[0041] Figures 10 and 11 are cross-sectional views showing further embodiments of a damper member.

[0042] Fig. 12 is a schematic diagram showing an example in which a damper member is provided in the first straight section and the second straight section of the loop pipe.

[0043] Fig. 13 is a schematic diagram showing an example in which a damper member is provided on a curved portion of a loop pipe.

[0044] Hereinafter, a compressor according to the present invention will be described in detail based on an embodiment illustrated in the attached drawings. Compressors can be classified into various types, such as rotary compressors, scroll compressors, and reciprocating compressors, depending on the compression method and the type of refrigerant used. However, this embodiment will be described using a reciprocating compressor as an example. However, the present invention is not limited to reciprocating compressors and can be equally applied to compressors equipped with loop pipes.

[0045] In addition, the reciprocating compressor may have a suction muffler and a discharge muffler that are independently provided, or may be connected to each other to form a single muffler assembly. This embodiment is described focusing on a reciprocating compressor in which the suction muffler and the discharge muffler form a single muffler assembly. However, the present invention is not limited thereto, and can be equally applied to a reciprocating compressor in which the suction muffler and the discharge muffler are independently provided.

[0046] In the following description, the side facing the compression chamber with the piston as the center is defined as the front, and the opposite side as the rear. In connection with this, the muffler assembly is described by defining the side facing the shell as the front, and the side facing away from the shell as the rear.

[0047] Fig. 1 is a perspective view showing the inside of the upper shell of a reciprocating compressor according to the present embodiment, and Fig. 2 is a cross-sectional view showing the inside of the reciprocating compressor of Fig. 1.

[0048] Referring to FIGS. 1 and 2, a reciprocating compressor according to the present embodiment may include a shell (110) forming an exterior, an electric motor (120) provided in an internal space (110a) of the shell (110) and providing driving force, a compression unit (130) receiving driving force from the electric motor (120) to compress refrigerant, and a suction / discharge unit (140) guiding refrigerant to a compression chamber (130a) and discharging the compressed refrigerant.

[0049] The shell (110) may include a lower shell (111) and an upper shell (112). The lower shell (111) and the upper shell (112) may be combined to form a sealed internal space (110a). The internal space (110a) of the shell (110) may accommodate a power unit (120) and a compression unit (130). The shell (110) may be made of a lightweight aluminum alloy with a high thermal conductivity.

[0050] The lower shell (111) may be formed in an approximately hemispherical shape. A suction pipe (115), a discharge pipe (116), and a process pipe (117) may be respectively penetrated and joined to the lower shell (111). These suction pipes (115), discharge pipes (116), and process pipes (117) may each be joined to the lower shell (111) by an insert die casting method.

[0051] The upper shell (112) can be formed in a roughly hemispherical shape like the lower shell (111). The upper shell (112) can be joined to the lower shell (111) on the upper side of the lower shell (111) to form the internal space (110a) of the shell (110) described above.

[0052] Referring to FIGS. 1 and 2, the electric motor (or drive motor) (120) according to the present embodiment may include a stator (121) and a rotor (122). The stator (121) may be elastically supported against the inner space (110a) of the shell (110), i.e., the bottom surface of the lower shell (111), and the rotor (122) may be rotatably installed inside the stator (121).

[0053] The stator (121) may include a stator core (1211) and a stator coil (1212).

[0054] The stator core (1211) is made of a metal material such as electrical steel, and when voltage is applied from the outside to the electric part (120), it performs electromagnetic interaction through electromagnetic force together with the stator coil (1212) and rotor (122) described later.

[0055] The stator core (1211) is formed in a roughly rectangular shape. For example, the inner circumference of the stator core (1211) may be formed in a circular shape, and the outer circumference may be formed in a rectangular shape. The stator core (1211) may be fixed to the lower surface of a cylinder block (131), which will be described later, by a stator fastening bolt (not shown).

[0056] The stator core (1211) can be flexibly supported by a support spring (123) at the lower end of the stator core (1211) relative to the bottom surface of the shell (110) while being spaced apart axially and radially from the inner surface of the shell (110). Accordingly, vibrations generated during operation can be suppressed from being directly transmitted to the shell (110).

[0057] The stator coil (1212) may be wound inside the stator core (1211). As described above, when voltage is applied from the outside, the stator coil (1212) generates an electromagnetic force and performs an electromagnetic interaction with the stator core (1211) and the rotor (122). Through this, the electric motor (120) generates a driving force for the reciprocating motion of the compression unit (130).

[0058] The rotor (122) may include a rotor core (1221) and a magnet (1222).

[0059] The rotor core (1221), like the stator core (1211), is made of a metal material such as electrical steel and can be formed into a roughly cylindrical shape. A drive shaft (125), which will be described later, can be press-fitted and joined to the center of the rotor core (1221).

[0060] The magnet (1222) is made of a permanent magnet and can be inserted and coupled at equal intervals along the circumference of the rotor core (1221). When voltage is applied, the rotor (122) rotates through electromagnetic interaction with the stator core (1211) and the stator coil (1212). Accordingly, the driving shaft (125) rotates together with the rotor (122) and transmits the rotational power of the electric part (120) to the compression part (130) through the connecting rod (126).

[0061] Referring to FIGS. 1 and 2, the compression unit (130) according to the present embodiment may include a cylinder block (131) and a piston (132). The cylinder block (131) is elastically supported on a shell (110), and the piston (132) is coupled to a drive shaft (125) by a connecting rod (126) and moves relative to the cylinder block (131).

[0062] The cylinder block (131) may be provided on one axial side of the electric motor (120), for example, on the upper side. The cylinder block (131) is fastened to the stator (121) with a stator fastening bolt (not shown), and may be elastically supported on the lower shell (111) together with the stator (121) of the electric motor (120).

[0063] The cylinder block (131) according to the present embodiment may include a frame portion (1311), a fixed projection portion (1312) coupled to a stator (121) of an electric unit (120), a shaft portion (1313) supporting a driving shaft (125), and a cylinder portion (hereinafter, abbreviated as cylinder) (1315) forming a compression chamber (130a).

[0064] The frame portion (1311) may be formed in a flat shape extending in the transverse direction, or may be formed in a radial shape by having a portion of the edge except for the corners processed to be thin.

[0065] The fixed protrusion (1312) may be formed at the edge of the frame portion (1311). For example, the fixed protrusion (1312) may be formed to protrude downward from the edge of the frame portion (1311) toward the electric unit (120). A fastening hole (1312a) may be formed in the fixed protrusion (1312) so that a stator fastening bolt (not shown) and a rear damper (152) to be described later are coupled thereto.

[0066] The shaft member (1313) can be formed to extend axially on both sides from the central portion of the frame member (1311). An shaft hole (1313a) is formed to penetrate the shaft member (1313) in the axial direction so that the drive shaft (125) can pass through it, and a bushing bearing can be inserted and coupled to the inner circumferential surface of the shaft hole (1313a).

[0067] A drive shaft (125) is axially supported on the upper end of the axle member (1313), and a drive shaft (125) can be radially supported on the inner circumferential surface of the axle member (1313). Accordingly, the drive shaft (125) can be axially and radially supported by the cylinder block (131).

[0068] The cylinder (1315) may be formed radially eccentrically from one edge of the frame portion (1311). The cylinder (1315) may be radially penetrated, and a piston (132) connected to a connecting rod (126) may be inserted into the inner opening, and a valve assembly (141) forming a suction / discharge portion (140) to be described later may be mounted on the outer opening.

[0069] The piston (132) may be formed flat with an open side (rear side) facing the connecting rod (126), while the opposite side (front side) facing away from the connecting rod (126) is closed. Accordingly, the connecting rod (126) is inserted into the rear side of the piston (132) and rotatably coupled, and the front side of the piston (132) forms a compression chamber (130a) inside the cylinder (1315) together with the valve assembly (141) described later.

[0070] Referring to FIGS. 1 and 2, the suction / discharge unit (140) according to the present embodiment may include a valve assembly (141), a muffler assembly (142), and a clamping member (143).

[0071] The valve assembly (141) may include an intake valve portion (not shown) and a discharge valve portion (not shown). The intake valve portion may connect the compression chamber (130a) to an intake connection groove (not shown) of a connecting muffler (not shown) to be described later, and the discharge valve portion may connect the compression chamber (130a) to an exhaust connection groove (not shown) of a connecting muffler (not shown) to be described later. Accordingly, the intake valve portion and the discharge valve portion may be formed to be adjacent to each other on a plane.

[0072] The muffler assembly (142) may include an intake muffler (142a) and a discharge muffler (142b). In other words, the muffler assembly (142) may be formed by combining an upper muffler and a lower muffler to form an intake space (S1) of the intake muffler (142a) and an discharge space (S2) of the discharge muffler (142b), respectively.

[0073] A discharge projection (mitoshi) formed in a hollow shape is formed on one side of the discharge muffler (142b), specifically, on the lower side of the discharge muffler, and one end of a loop pipe (118) for connecting the discharge muffler (142b) to the discharge pipe (116) can be connected to the discharge projection. In other words, a loop pipe (118) that guides the refrigerant in the discharge space (S2) to the discharge pipe (116) is connected between the discharge projection of the discharge muffler (142b) and the discharge pipe (116).

[0074] In this case, a damper member (160), which will be described later, may be inserted into the outer surface of the loop pipe (118). The damper member (160) may be formed of an elastic material, such as rubber, having a lower rigidity than the loop pipe (118). Accordingly, the damper member (160) may absorb and reduce vibration of the loop pipe (118) by being deformed by the vibration of the loop pipe (118). The damper member (160) will be described again later together with the loop pipe (118).

[0075] The clamping member (143) is provided at the front of the suction / discharge portion (140), that is, at the front surface of the muffler assembly (142), so as to fix the muffler assembly (142) to the cylinder block (131) of the compression portion (130).

[0076] The damping unit (150) is provided on the upper side of the compression unit (130) and the suction / discharge unit (140). The damping unit (150) may include a front damper (151) and a rear damper (152) which are respectively provided on both sides of the reciprocating direction of the piston (132), and the front damper (151) and the rear damper (152) may be made of an elastic material such as rubber. The front damper (151) can effectively suppress or buffer the impact caused by the collision between the compression unit (130) and the suction / discharge unit (140) and the shell (110) when the compressor is driven. The rear damper (152) can effectively suppress or buffer the impact caused by the collision between the shell (110) and the compression unit (130) when the compressor is driven.

[0077] In the drawing, the unexplained symbol 1251 is the oil path, 1255 is the oil feeder, and 127 is the balance weight.

[0078] The reciprocating compressor according to the above embodiment operates as follows.

[0079] That is, when power is applied to the electric motor (120), the rotor (122) rotates. When the rotor (122) rotates, the drive shaft (125) coupled to the rotor (122) rotates and transmits the rotational force to the piston (132) through the connecting rod (126). The piston (132) reciprocates in the forward and backward direction with respect to the cylinder (1315) by the connecting rod (126).

[0080] For example, when the piston (132) moves backward (suction stroke) in the cylinder (1315), the volume of the compression chamber (130a) increases. When the volume of the compression chamber (130a) increases, the refrigerant filled in the suction space (S1) of the muffler assembly (142) through the suction pipe (115) passes through the suction valve section of the valve assembly (141) and is sucked into the compression chamber (130a).

[0081] Conversely, when the piston (132) moves forward (discharge stroke) in the cylinder (1315), the volume of the compression chamber (130a) is reduced. When the volume of the compression chamber (130a) is reduced, the refrigerant filled in the compression chamber (130a) is compressed and discharged through the discharge valve part of the valve assembly (141) into the discharge connection groove of the connecting muffler, and the refrigerant is discharged into the discharge space (S2) forming the discharge muffler (142b) and then discharged into the refrigeration cycle through the discharge pipe (116) via the loop pipe (118), repeating a series of processes.

[0082] Typically, in the case of a reciprocating compressor, since the loop pipe (118) connects the discharge muffler (142b) of the compression section (130) and the discharge pipe (116), vibrations generated in the compression section (130) during operation of the compressor may be transmitted to the outside of the compressor through the loop pipe (118). Considering this, as previously described, technologies have been proposed to reduce vibrations in the loop pipe by wrapping a steel spring around a steel loop pipe, applying a plastic loop pipe, or using a plurality of vibration reduction sleeves. However, as previously described, these conventional vibration reduction technologies each have their own limitations.

[0083] Accordingly, in this embodiment, a damper member (160) made of an elastic material is inserted into the loop pipe (118), and the inner diameter (D2) of the damper member (160) is formed to be larger than the outer diameter (D1) of the loop pipe (118), so that when the loop pipe (118) vibrates, the damper member (160) is radially deformed to absorb the vibration.

[0084] Fig. 3 is a perspective view showing the installation state of a damper member according to the present embodiment, Fig. 4 is a cross-sectional view taken along line “Ⅸ-Ⅸ” of Fig. 3, and Fig. 5 is a schematic diagram showing an example in which a damper member is installed on a first straight portion of a loop pipe.

[0085] Referring to FIGS. 3 to 5, the loop pipe (118) according to the present embodiment connects between the discharge muffler (142b) and the discharge pipe (116) as described above, but may be extended so that at least a portion thereof is immersed in the oil stored in the internal space (110a) of the shell (110).

[0086] For example, the loop pipe (118) may be made of steel or a synthetic resin material such as plastic. This embodiment focuses on an example in which the loop pipe (118) is made of steel. This reduces the material cost for the loop pipe (118) and reduces manufacturing costs due to the ease of welding.

[0087] Specifically, the loop pipe (118) may be formed into a shape having one or more straight sections (118a, 118b) and one or more curved sections (118c). In other words, the loop pipe (118) may be formed by being bent several times along the inner circumference of the shell (110). Accordingly, the loop pipe (118) may be extended as long as possible to minimize vibration transmitted from the compression section (130).

[0088] In addition, the loop pipe (118) may be formed so that the outer diameter (D1) between both ends is the same or nearly the same. Accordingly, not only can the pressure change of the refrigerant discharged through the loop pipe (118) be minimized, but also the assembly and / or movement stability of the damper member (160) described later can be increased.

[0089] Referring to FIG. 5, the damper member (160) according to the present embodiment may be provided to surround at least a portion of the loop pipe (118). In other words, the damper member (160) may be formed to surround the straight portion (118a, 118b) and / or the curved portion (118c) of the loop pipe (118). Accordingly, the damper member (160) can reduce the vibration generated in the compression portion (130) from being transmitted to the discharge pipe (116) through the loop pipe (118).

[0090] For example, the damper member (160) according to the present embodiment may be provided to surround the longest first straight portion (118a) of the loop pipe (118). Accordingly, the damper member (160) is formed to be long in correspondence with the length of the first straight portion (118a) of the loop pipe (118), and can effectively attenuate vibration transmitted through the loop pipe (118).

[0091] In this case, the damper member (160) may be formed of a material having a stiffness lower than that of the loop pipe (118), for example, the damper member (160) may be formed of an elastic material such as rubber. Accordingly, the damper member can effectively absorb and attenuate vibrations transmitted through the loop pipe (118).

[0092] In addition, the damper member (160) may be formed in a smooth pipe shape with a circular inner surface. In other words, the loop pipe (118) may be formed in a circular cross-section shape, and the damper member (160) may be formed in a circular cross-section shape similar to that of the loop pipe (118). Accordingly, the manufacturing and / or assembly of the damper member (160) may be facilitated.

[0093] Although not shown in the drawing, the inner surface of the damper member (160) is formed to be smooth, but may also be formed in other shapes such as an oval cross-section shape, a triangular cross-section shape, a square cross-section shape, etc. In these cases, the damping effect can be increased by forming an empty space filled with oil between the inner surface of the damper member (160) and the outer surface of the loop pipe (118) while minimizing the outer diameter (D1) of the damper member (160).

[0094] In addition, the inner diameter (D2) of the damper member (160) may be formed to be larger than the outer diameter (D1) of the loop pipe (118). In other words, the damper member (160) may be provided to hang and wrap around the outer surface of the loop pipe (118). Accordingly, when the loop pipe (118) vibrates, the damper member (160) may vibrate radially with the loop pipe (118) as the center, thereby attenuating the vibration of the loop pipe (118).

[0095] In this case, since an impact occurs when the inner surface of the damper member (160) collides with the outer surface of the loop pipe (118), it may be advantageous in terms of vibration damping to form the damper member (160) as thick as possible. For example, the thickness of the damper member (160) may be formed to be thicker than the thickness of the loop pipe (118).

[0096] Also, in this case, the loop pipe (118) may be provided with a stopper (170) to limit the movement of the damper member (160) in the longitudinal direction of the loop pipe (118). In other words, since the inner diameter (D2) of the damper member (160) is formed to be larger than the outer diameter (D1) of the loop pipe (118), the damper member (160) can move freely in the loop pipe (118). In this case, vibration noise may be generated when the damper member (160) collides with surrounding components including the loop pipe (118) and / or the shell (110). Therefore, stoppers (170) may be provided on both sides of the longitudinal direction of the damper member (160) to limit the longitudinal movement of the damper member (160). Accordingly, the inner diameter (D2) of the damper member (160) is formed to be larger than the outer diameter (D1) of the loop pipe (118), and the longitudinal movement of the damper member (160) is restricted, thereby suppressing vibration noise caused by collision between the damper member (160) and surrounding members.

[0097] For example, the stopper (170) may be formed as a snap ring as illustrated in FIG. 5. In this case, a pair of stoppers (170) positioned on opposite sides in the longitudinal direction with respect to the damper member (160) may be snap-fitted and connected to the loop pipe (118) on both sides of the damper member (160), respectively. Accordingly, the stopper (170) can be easily assembled while stably restricting the longitudinal movement of the damper member (160).

[0098] In the reciprocating compressor as described above, vibration generated during operation of the compressor may be transmitted to the discharge pipe (116) through the loop pipe (118), thereby causing vibration of the compressor. However, as in this embodiment, since a damper member (160) is provided in the middle of the loop pipe (118), that is, in the first straight portion (118a) of the loop pipe (118), the damper member (160) can absorb and cancel out the vibration transmitted to the loop pipe (118). Through this, vibration generated on the discharge side of the compression unit (130) is blocked from being transmitted to the discharge pipe (116) through the discharge muffler (142b) and the loop pipe (118), thereby reducing the vibration noise of the compressor.

[0099] In this case, since the damper member (160) is formed of an elastic material, the damper member (160) can effectively absorb and reduce the vibration of the loop pipe (118) by deforming according to the vibration of the loop pipe (118).

[0100] In addition, in the case where the inner diameter (D2) of the damper member (160) is formed to be larger than the outer diameter (D1) of the loop pipe (118) as in the present embodiment, the damper member (160) vibrates in the range indicated by the dotted line in FIG. 4, and due to this vibration, the damper member (160) is elastically deformed to a greater extent, so that the vibration reduction effect can be further improved.

[0101] FIG. 6 and FIG. 7 are graphs comparing the vibration reduction effect of a reciprocating compressor equipped with a damper member according to the present invention with a case without a conventional damper member and a case equipped with a damper member made of a steel spring, respectively. FIG. 6 is a graph comparing vibration in the operating range of a reciprocating compressor, and FIG. 7 is a graph comparing vibration in the full range.

[0102] Referring to Fig. 6, it can be seen that in the case of having a damper member according to the present embodiment, a superior vibration reduction effect is exhibited in the operating range of the compressor compared to the case where the damper member is not provided (conventional ①). In the case of a conventional steel spring (conventional ②), a superior vibration reduction effect is exhibited in the operating range of the compressor compared to the case where the damper member is not provided. However, in the case of a steel spring (conventional ②), it can be seen that the amplitude (magnitude of acceleration, ACC) in high-speed operation is relatively large compared to the case where the damper member according to the present embodiment is provided. Through this, it can be seen that inserting a damper member (160) made of an elastic material and having an inner diameter (D2) larger than the outer diameter (D1) of the loop pipe (118) so as to be hung on the loop pipe (118) as in the present embodiment is the most advantageous in terms of vibration reduction.

[0103] Referring to Fig. 7, it can be seen that in the case where the damper member (160) according to the present embodiment is provided, the amplitude (magnitude of acceleration, ACC) in the entire band exhibits a superior vibration reduction effect compared to the case where the damper member is not provided (conventional ①). In particular, in the case of the conventional steel spring (conventional ②), it can be seen that vibration is more severe than in the case where the damper member is not provided as well as in the present embodiment in the high-frequency band of approximately 1,000 Hz. Through this, it can be seen that in the case where the damper member (160) of the present embodiment is inserted into the loop pipe (118), the vibration reduction effect is excellent not only in the aforementioned operating range but also throughout the entire band.

[0104] Meanwhile, there are other examples of damper members as follows.

[0105] That is, in the above-described embodiment, the inner surface of the damper member is formed in a smooth pipe shape, but in some cases, a damping protrusion may be formed on the inner surface of the damper member.

[0106] Fig. 8 is a cross-sectional view showing another embodiment of a damper member.

[0107] Referring to FIG. 8, the damper member (160) according to the present embodiment is made of a material having less rigidity than the loop pipe (118), that is, an elastic material such as rubber, and the inner diameter of the damper member (160) is formed to be larger than the outer diameter of the loop pipe (118) so that it can be inserted so as to be hung on the loop pipe (118). In this case, stoppers (170) are provided on both sides of the damper member (160) so that the longitudinal movement of the damper member (160) can be restricted. The basic configuration and the resulting operational effects of the loop pipe (118), the damper member (160), and the stopper (170) are the same as or almost similar to those in the above-described embodiment, and therefore, the description thereof will be replaced with the description of the above-described embodiment.

[0108] However, in the present embodiment, at least one damping protrusion (160a) may be formed on the inner surface of the damper member (160). For example, a plurality of damping protrusions (160a) may be formed along the inner surface of the damper member (160). In this case, the plurality of damping protrusions (160a) may be formed with the same shape and / or size and arranged at equal intervals along the inner surface of the damper member (160). Accordingly, even if the damper member (160) rotates on the outer surface of the loop pipe (118) when the loop pipe (118) vibrates, a uniform damping force can be secured.

[0109] In this case, the minimum diameter (D3) of the virtual circle (C) connecting the inflection points of the damping protrusions (160a) can be formed to be larger than or equal to the outer diameter (D1) of the loop pipe (118). In the former case, the damping protrusion (160a) is formed on the inner surface of the damper member (160), but the damper member (160) is not restricted by the loop pipe (118) and is deformed as much as possible by centrifugal force, thereby increasing the vibration reduction effect, whereas in the latter case, a high damping effect can be obtained when the installation space of the damper member (160) is narrow or when driving at low speeds. In this embodiment, an example is shown in which the minimum diameter of the virtual circle of the damping protrusion (160a) is formed to be larger than the outer diameter (D1) of the loop pipe (118).

[0110] In addition, although the present embodiment illustrates an example in which the damping protrusion (160a) has a circular cross-section shape, it is not limited thereto. For example, the damping protrusion (160a) may be formed in a triangular cross-section shape or a diamond cross-section shape.

[0111] In the case where a plurality of damping protrusions (160a) are formed along the inner surface of the damper member (160) as described above, when the damper member (160) is deformed, the damping protrusions (160a) can cushion the impact between the damper member (160) and the loop pipe (118) and thereby reduce the impact. Through this, damage to the loop pipe (118) and / or the damper member (160) can be suppressed, thereby increasing reliability.

[0112] In addition, in this case, the oil stored in the internal space (110a) of the shell (110) can be accommodated in the gap between the damping protrusions (160a) of the damper member (160). Through this, as the weight of the damper member (160) increases, the vibration reduction capability of the damper member (160) can be further improved.

[0113] Meanwhile, another embodiment of the damper member is as follows.

[0114] That is, in the above-described embodiment, the damper member is formed of a single material, but in some cases, the damper member may be formed of multiple materials.

[0115] Fig. 9 is a cross-sectional view showing another embodiment of a damper member.

[0116] Referring to FIG. 9, the damper member (160) according to the present embodiment is made of a material having less rigidity than the loop pipe (118), that is, an elastic material such as rubber, and the inner diameter of the damper member (160) is formed to be larger than the outer diameter of the loop pipe (118) so that it can be inserted so as to be hung on the loop pipe (118). In this case, stoppers (170) are provided on both sides of the damper member (160) so that the longitudinal movement of the damper member (160) can be restricted. The basic configuration and the resulting operational effects of the loop pipe (118), the damper member (160), and the stopper (170) are the same as or almost similar to those in the above-described embodiment, and therefore, the description thereof will be replaced with the description of the above-described embodiment.

[0117] However, the damper member (160) according to the present embodiment may be formed of different materials. For example, the damper member (160) may include a first damping portion (161) that wraps around the loop pipe (118) and a second damping portion (162) that wraps around the first damping portion (161). The first damping portion (161) may be formed of an elastic material having a lower rigidity than the loop pipe (118), and the second damping portion (162) may be formed of a material that is heavier than the first damping portion (161). In other words, the first damping portion may be formed of a rubber material as in the above-described embodiments, and the second damping portion (162) may be formed of a metal material such as steel. Accordingly, the vibration reduction effect may be increased without significantly increasing the outer diameter of the damper member (160).

[0118] In this case, the thickness of the first damping portion (161) may be formed to be greater than or equal to the thickness of the second damping portion (162). In the former case, the cushioning effect of the damper member (160) can be increased as the thickness of the first damping portion (161) made of an elastic material is formed thick, and in the latter case, the weight of the damper member (160) can be increased as the heavy second damping portion (162) is formed relatively thick. This embodiment illustrates an example in which the thickness of the first damping portion (161) is formed thicker than the thickness of the second damping portion (162).

[0119] As described above, when the damper member (160) is formed of different materials, with the inner surface being formed of an elastic material and the outer surface being formed of a heavy material, the vibration reduction effect can be increased by increasing the weight of the damper member (160) without increasing the size of the damper member (160). Through this, even if the inner space (110a) of the shell (110) is narrow, such as in a small reciprocating compressor, interference between the damper member (160) and other surrounding components can be minimized, thereby increasing the vibration reduction effect and / or reliability.

[0120] Although not shown in the drawing, at least one fixing projection (not shown) may be formed on the outer surface of the first damping portion (161) and / or the inner surface of the second damping portion (162), and at least one fixing groove (not shown) into which the fixing projection is inserted may be formed on the inner surface of the second damping portion (162) facing the first damping portion (161) and / or the outer surface of the first damping portion (161). In this case, the bonding force between the first damping portion (161) and the second damping portion (162) can be increased.

[0121] Meanwhile, another embodiment of the damper member is as follows.

[0122] That is, in the above-described embodiment, the damper member is formed in a single tube shape, but in some cases, the damper member may be formed in a coil shape or a plurality of ring shapes.

[0123] Figures 10 and 11 are cross-sectional views showing further embodiments of a damper member.

[0124] Referring to FIGS. 10 and 11, the damper member (160) according to the present embodiment is made of a material having less rigidity than the loop pipe (118), that is, an elastic material such as rubber, and the inner diameter of the damper member (160) is formed to be larger than the outer diameter of the loop pipe (118) so that it can be inserted so as to be hung on the loop pipe (118). In this case, stoppers (170) are provided on both sides of the damper member (160) so that the longitudinal movement of the damper member (160) can be restricted. The basic configuration and the resulting operational effects of the loop pipe (118), the damper member (160), and the stopper (170) are the same as or almost similar to those in the above-described embodiment, and therefore, the description thereof will be replaced with the description of the above-described embodiment.

[0125] However, unlike the aforementioned embodiment which is in the form of a tube, the damper member (160) according to the present embodiment may be formed in a coil shape as shown in Fig. 10. In other words, the damper member (160) may be formed in a shape that is spirally wound around the outer surface of the loop pipe (118).

[0126] In the case where the damper member (160) is formed in a coil shape as described above, vibration in a direction perpendicular to the longitudinal direction of the loop pipe (118), for example, in the Y direction and the Z direction, can be reduced when the compressor is operated, and vibration in the X direction, which is the longitudinal direction of the loop pipe (118), can also be reduced by causing friction and deformation as the damper member (160) expands in the longitudinal direction of the loop pipe (118).

[0127] This can achieve almost the same effect even when the damper member (160) is formed in a plurality of ring shapes as in FIG. 11. For example, the damper member 160) can be formed of a plurality of rings. In this case, the plurality of rings forming the damper member (160) can be arranged along the longitudinal direction of the loop pipe (118) so that a slight gap is formed between each ring. Accordingly, even when the damper member (160) is formed of a plurality of rings as in the embodiment of FIG. 10 formed in a coil shape, each damper member (160) can rub against and deform in the longitudinal direction of the loop pipe (118) when the compressor is operating. This can reduce three-directional vibrations including not only the directions orthogonal to the longitudinal direction of the loop pipe (118) but also the longitudinal direction of the loop pipe (118).

[0128] Meanwhile, another embodiment of the damper member is as follows.

[0129] That is, in the above-described embodiments, the damper member is provided on a straight portion extending in the X direction of the loop pipe, but in some cases, the damper member may be provided on a straight portion extending in another direction, for example, not only in the X direction but also in the Y direction and / or the Z direction.

[0130] Fig. 12 is a schematic diagram showing an example in which a damper member is provided in the first straight section and the second straight section of the loop pipe.

[0131] Referring to FIG. 12, the damper member (160) according to the present embodiment is made of a material having less rigidity than the loop pipe (118), that is, an elastic material such as rubber, and the inner diameter of the damper member (160) is formed to be larger than the outer diameter of the loop pipe (118) so that it can be inserted so as to be hung on the loop pipe (118). In this case, stoppers (170) are provided on both sides of the damper member (160) so that the longitudinal movement of the damper member (160) can be restricted. The basic configuration and the resulting operational effects of the loop pipe (118), the damper member (160), and the stopper (170) are the same as or almost similar to those in the above-described embodiments, and therefore, the description thereof will be replaced with the description of the above-described embodiments.

[0132] However, in the present embodiment, the damper member (160) may be divided into a plurality of pieces and inserted into the loop pipe (118) in different directions. For example, the loop pipe (118) may include a first straight portion (118a) extending in the X direction and a second straight portion (118b) extending in the Z direction. In this case, the first damper member (165) may be inserted into the first straight portion (118a) so as to be suspended, and the second damper member (166) may be inserted into the second straight portion (118b) so as to be suspended. These first damper members (165) and second damper members (166) may be formed in the same manner as in the embodiments of FIG. 3 to FIG. 9 described above.

[0133] In the case where a first damper member (165) is provided in the first straight portion (118a) extending in the X direction as described above, and a second damper member (166) is provided in the second straight portion (118b) extending in the Z direction, a vibration reduction effect can be obtained in three directions of the loop pipe (118).

[0134] For example, the first damper member (165) can obtain a vibration reduction effect in the Y and Z directions as in the embodiment of Fig. 5, and the second damper member (166) can obtain a vibration reduction effect in the X and Z directions. Through this, the effect of reducing all three-directional vibrations of the loop pipe (118), i.e., vibrations in the X, Y, and Z directions, can be obtained.

[0135] Although not shown in the drawing, in some cases, only the second damper member (166) may be installed in the second straight section (118b). In this case, as described above, a vibration reduction effect in the X and Z directions can be obtained.

[0136] In addition, although not shown in the drawing, in some cases, a damper member (not shown) may also be provided on the Y-direction straight section forming the third straight section (not shown). However, in this case, the stopper (170) may be formed large or the inner diameter of the damper member may be formed relatively small so as to prevent the damper member from flowing down excessively.

[0137] Meanwhile, another embodiment of the damper member is as follows.

[0138] That is, in the embodiments described above, the damper member is provided on the straight portion of the loop pipe, but in some cases, the damper member may also be provided on the curved portion.

[0139] Fig. 13 is a schematic diagram showing an example in which a damper member is provided on a curved portion of a loop pipe.

[0140] Referring to FIG. 13, the damper member (160) according to the present embodiment is made of a material having less rigidity than the loop pipe (118), that is, an elastic material such as rubber, and the inner diameter of the damper member (160) is formed to be larger than the outer diameter of the loop pipe (118) so that it can be inserted to be hung on the loop pipe (118).

[0141] In this case, stoppers (170) are provided on both sides of the damper member (160) so that the longitudinal movement of the damper member (160) can be restricted. The basic configuration and the resulting operational effects of the loop pipe (118), damper member (160), and stopper (170) are the same as or almost similar to those in the above-described embodiments, and therefore, the description thereof will be replaced with the description of the above-described embodiments.

[0142] However, in the present embodiment, the third damper member (167) may be provided in the curved portion (118c) of the loop pipe (118). For example, the loop pipe (118) may have a curved portion (118c) formed between a first straight portion (118a) extending in the X direction and a second straight portion (118b) extending in the Z direction. In this case, the third damper member (167) may be formed in a curved shape along the shape of the curved portion (118c) of the loop pipe (118).

[0143] In the case where the third damper member (167) is provided in the curved portion (118c) of the loop pipe (118) as described above, vibrations in all three directions, namely the X direction, Y direction, and Z direction, can be reduced with a single third damper member (167). Accordingly, the installation space for the third damper member (167) can be minimized while increasing the vibration reduction effect in various directions.

[0144] Also, in this case, the third damper member (167) may be provided only on the curved portion (118c), or may be formed long enough to surround the first straight portion (118a) and / or the second straight portion (118b) extending from the curved portion (118c). In the former case, as described above, the vibration reduction effect in various directions can be increased while minimizing the length of the third damper member (167), and in the latter case, the vibration reduction effect in each direction can be further increased.

[0145] Although not shown in the drawing, the third damper member (167) provided in the curved portion (118c) may be separated from the first damper member (165) provided in the first straight portion (118a) and / or the second damper member (166) provided in the second straight portion (118b). In this case, the assembly of the damper members (165), (166), and (167) can be facilitated while also increasing the vibration reduction effect.

Claims

1. Shell; A compression unit provided in the internal space of the above shell and compressing the refrigerant; A discharge pipe provided to penetrate the above shell; A loop pipe that guides the compressed refrigerant in the above compression section to a discharge pipe; and Including a damper member surrounding at least a portion of the above loop pipe, The above damper member, A compressor formed of a material having a rigidity smaller than that of the above loop pipe.

2. In paragraph 1, The above damper member, A compressor formed from an elastic material.

3. In paragraph 1, The above damper member, A compressor whose inner diameter is formed larger than the outer diameter of the above loop pipe.

4. In paragraph 1, The above damper member, A compressor formed into a smooth tube shape with a circular or oval inner surface.

5. In paragraph 1, The above damper member, A compressor having at least one damping projection formed on its inner surface.

6. In paragraph 5, The above damping protrusions are formed in multiple numbers along the inner surface of the damper member, The minimum diameter of the virtual circle connecting the above multiple damping projections is A compressor formed to have an outer diameter greater than or equal to that of the above loop pipe.

7. In paragraph 1, The above damper member, A compressor formed in a tube shape, a coil shape, or a plurality of ring shapes.

8. In paragraph 1, The above damper member, A first damping member surrounding the above loop pipe; and Including a second damping part surrounding the first damping part, The above second damping part, A compressor formed of a material heavier than the first damping section.

9. In paragraph 8, The thickness of the above first damping part is A compressor formed to have a thickness greater than or equal to that of the second damping section.

10. In any one of paragraphs 1 to 9, The above loop pipe includes a straight section and a curved section, The above damper member, A compressor inserted into at least one of the straight and curved sections of the above loop pipe.

11. In paragraph 10, A compressor in which a stopper is provided in the above loop pipe to limit movement of the damper member in the longitudinal direction of the above loop pipe.

12. In paragraph 10, A certain amount of oil is stored in the internal space of the above shell, The above damper member, A compressor provided so that at least a portion of the compressor is immersed in said oil.

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