Compressor

Abstract

A reciprocating compressor is disclosed. The reciprocating compressor comprises a shell, a compression section, a discharge pipe, a loop pipe, and a damper member, wherein the damper member may be formed of a material having a stiffness less than that of the loop pipe and may be provided to surround at least a portion of the loop pipe. Through this, when the compressor operates and the loop pipe vibrates, the damper member surrounding the loop pipe deforms due to the vibration of the loop pipe, thereby absorbing and reducing the vibration of the loop pipe.

Description

Technology Field

[0001] The present invention relates to a compressor. Background Technology

[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. Additionally, compressors can be classified into direct discharge and indirect discharge methods based on the refrigerant discharge method. The former is a method in which the refrigerant discharged from the compression chamber is directly connected to a discharge pipe for discharge, while the latter is a method in which the refrigerant discharged from the compression chamber passes through the internal space of a shell before being discharged through a discharge pipe. This invention relates to the former, namely the direct discharge method.

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

[0004] Reciprocating compressors can be classified into vibrating and connected types based on the piston driving method. A vibrating reciprocating compressor is a method in which a piston is connected to the actuator of a reciprocating motor and compresses the refrigerant by reciprocating within a cylinder while vibrating. A connected reciprocating compressor is a method in which a piston is connected to the rotating shaft of a rotary motor and compresses the refrigerant by reciprocating within a cylinder. In the following, the reciprocating compressor can be defined as a connected reciprocating compressor.

[0005] This type of reciprocating compressor is structured such that a compressor section for compressing the refrigerant and an electric motor section providing driving force to the compressor section are housed within a sealed shell. A discharge pipe is connected through the shell, and the refrigerant compressed in the compressor section is guided to the discharge pipe through the previously described loop pipe and discharged to the outside.

[0006] In such reciprocating compressors, vibrations generated during the operation of the compressor section can be transmitted to the outside through the loop pipe. Therefore, it is important to minimize vibrations transmitted through the loop pipe. In particular, with the recent increase in the maximum operating speed of compressors, there is a problem where vibrations worsen as the loop pipe is designed with high rigidity to avoid resonance modes.

[0007] To solve this, 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 vibrations of the loop pipe by utilizing friction between the loop pipe and the spring.

[0008] However, while the method using steel springs can be effective in reducing vibrations in resonance modes, there is a problem in that additional vibrations are caused in the high-frequency range due to steel-to-steel contact between the loop pipe and the steel spring. Furthermore, although longer springs are more effective for vibration reduction, there are limitations to increasing the spring length due to the effect of lowering the resonance point caused by increased weight.

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

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

[0011] Meanwhile, Patent Document 2 (Chinese Published Patent No. 115523119) discloses a method for reducing vibration by covering a bend in the internal exhaust pipe of a gas compressor with a rubber vibration-reducing sleeve and supporting the rubber vibration-reducing sleeve using a plurality of springs and a fixing sheet.

[0012] The vibration reduction structure disclosed in Patent Document 2 requires combining multiple members into a complex structure, which results in cumbersome assembly work and increased production costs. Prior art literature

[0013] Published Patent No. 10-2005-0071259 (Publication Date: July 7, 2005) Chinese Published Patent No. 115523119 (Publication Date: December 27, 2022) The problem to be solved

[0014] The objective of the present invention is to provide a compressor capable of reducing vibration of the loop pipe not only in the compressor's operating range but also across the entire vibration frequency band.

[0015] Another objective of the present invention is to provide a compressor capable of effectively reducing the vibration of a loop pipe with a simple structure.

[0016] Another objective of the present invention is to provide a compressor capable of reducing vibration of a loop pipe at a low cost. means of solving the problem

[0017] To achieve the objective of the present invention, a compressor comprising a shell, a compression section, a discharge pipe, a loop pipe, and a damper member may be provided. The compression section may be provided in the internal space of the shell and may compress a refrigerant. The discharge pipe may be provided to penetrate the shell. The loop pipe may guide the refrigerant compressed in the compression section to the discharge pipe. The damper member may wrap around a portion of the loop pipe. The damper member may be formed of a material having a stiffness less than that of the loop pipe. Accordingly, when the compressor operates and the loop pipe vibrates, the damper member wrapping the loop pipe deforms due to the vibration of the loop pipe, thereby absorbing and reducing the vibration of the loop pipe.

[0018] For example, the damper member may be formed of an elastic material. By doing so, the deformation of the damper member increases, and the vibration reduction effect can be improved.

[0019] For example, the inner diameter of the damper member may be formed to be larger than the outer diameter of the loop pipe. Accordingly, the damper member vibrates around the loop pipe, and the vibration reduction effect can be further enhanced.

[0020] 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 superior vibration reduction effect can be obtained.

[0021] For example, the damper member may have at least one damping projection formed on its inner surface. Preferably, a plurality of damping projections are formed along the inner surface of the damper member, and the minimum diameter of the virtual circle connecting the plurality of damping projections may be formed to be greater than or equal to the outer diameter of the loop pipe.

[0022] The above damping protrusions can reduce vibrations in various directions of the loop pipe 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 increased due to the viscosity of the oil.

[0023] For example, the damper member may be formed in a tube shape, a coil shape, or a plurality of ring shapes.

[0024] If the 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 along the longitudinal direction of the loop pipe, and accordingly, not only vibrations in a direction perpendicular to the longitudinal direction of the loop pipe but also vibrations in a direction parallel to the longitudinal direction of the loop pipe can be reduced simultaneously.

[0025] For example, the damper member may include a first damping portion surrounding the loop pipe and a second damping portion surrounding 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.

[0026] As a result, the overall weight of the damping member is increased, thereby allowing for sufficient vibration reduction without significantly increasing the size of the damping member, and minimizing interference with other parts in the narrow space of the reciprocating compressor.

[0027] For example, the loop pipe may include a straight section and a curved section, and the damper member may be inserted into at least one of the straight section and the curved section of the loop pipe.

[0028] When the damper member is inserted into the straight section of the loop pipe, it can reduce vibration in a plane perpendicular to the longitudinal direction of the loop pipe, i.e., two-way vibration, and when the damper member is inserted into the curved section of the loop pipe, the vibration reduction effect is reduced, but it has the effect of reducing three-way vibration of the loop pipe.

[0029] For example, the loop pipe may be provided with a stopper to restrict the movement of the damper member along the longitudinal direction of the loop pipe. This prevents the damper member from moving to the curved portion of the loop pipe, particularly when the damper member is installed in the straight portion of the loop pipe, thereby reducing the vibration amplitude of the damper member and preventing a decrease in the vibration reduction effect.

[0030] For example, a predetermined amount of oil is stored in the internal space of the shell, and the damper member may be provided such that at least a portion of it is submerged in the oil. In this case, the viscosity of the oil can reduce the vibration of the loop pipe together with the damper member. Effects of the invention

[0031] The compressor according to the present invention is provided with 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 less than that of the loop pipe. By doing so, an excellent vibration reduction effect can be obtained not only in the operating range of the compressor but also in the entire vibration frequency range.

[0032] The compressor according to the present invention can have a damper member formed in the shape of a smooth tube with an inner surface that is circular or elliptical, so that it can effectively reduce vibration of the loop pipe with a very simple structure.

[0033] The compressor according to the present invention can reduce vibration of the loop pipe at a low cost by using a damper member in the form of a smooth tube made of an elastic member such as rubber. Brief explanation of the drawing

[0034] FIG. 1 is a perspective view showing the interior of a reciprocating compressor according to the present embodiment with the upper shell separated. FIG. 2 is a cross-sectional view showing the interior of the reciprocating compressor of FIG. 1. 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 along line "IX-IX" of FIG. 3. FIG. 5 is a schematic diagram illustrating an example in which a damper member is provided in the first straight section of a loop pipe. FIGS. 6 and FIGS. 7 are graphs comparing the vibration reduction effect of a reciprocating compressor equipped with a damper member according to the present invention with that of a conventional case without a damper member and a case equipped with a damper member made of a steel spring, respectively, where FIG. 6 shows the vibration in the operating range of the reciprocating compressor and FIG. 7 shows the vibration in the entire range. FIG. 8 is a cross-sectional view showing another embodiment of a damper member. FIG. 9 is a cross-sectional view showing another embodiment of a damper member. FIGS. 10 and FIGS. 11 are cross-sectional views showing other embodiments of a damper member. FIG. 12 is a schematic diagram illustrating an example in which a damper member is provided in the first straight section and the second straight section of a loop pipe. FIG. 13 is a schematic diagram illustrating an example in which a damper member is provided on a curved portion of a loop pipe. Specific details for implementing the invention

[0035] Hereinafter, a compressor according to the present invention will be described in detail based on an embodiment illustrated in the attached drawings. Although compressors can be classified into various forms such as rotary compressors, scroll compressors, and reciprocating compressors depending on the compression method and the type of refrigerant used, this embodiment is described using a reciprocating compressor as an example. However, it is not limited to reciprocating compressors and can be applied equally to compressors equipped with loop pipes.

[0036] In addition, the intake muffler and the discharge muffler of the reciprocating compressor may be provided independently, or they may be connected to form a single muffler assembly. This embodiment describes a reciprocating compressor in which the intake muffler and the discharge muffler form a single muffler assembly. However, it is not limited to this and can be equally applied to reciprocating compressors in which the intake muffler and the discharge muffler are provided independently.

[0037] In the following descriptions, the side facing the compression chamber is defined as the front and the opposite side as the rear, centered on the piston. Accordingly, 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.

[0038] FIG. 1 is a perspective view showing the interior of a reciprocating compressor according to the present embodiment with the upper shell separated, and FIG. 2 is a cross-sectional view showing the interior of the reciprocating compressor of FIG. 1.

[0039] Referring to FIGS. 1 and 2, the reciprocating compressor according to the present embodiment may include a shell (110) forming an exterior, an electric motor (120) provided in the internal space (110a) of the shell (110) and providing driving force, a compression unit (130) that receives driving force from the electric motor (120) and compresses a refrigerant, and a suction / discharge unit (140) that guides the refrigerant to a compression chamber (130a) and discharges the compressed refrigerant.

[0040] 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 driving unit (120) and a compression unit (130). The shell (110) may be made of a lightweight aluminum alloy with a high thermal conductivity.

[0041] The lower shell (111) can be formed in a roughly hemispherical shape. A suction pipe (115), a discharge pipe (116), and a process pipe (117) can each be connected to the lower shell (111) by penetrating through it. These suction pipe (115), discharge pipe (116), and process pipe (117) can each be connected to the lower shell (111) by an insert die-casting method.

[0042] The upper shell (112) can be formed in a roughly hemispherical shape, similar to the lower shell (111). The upper shell (112) can be coupled 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.

[0043] 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) is elastically supported against the internal 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).

[0044] The stator (121) may include a stator core (1211) and a stator coil (1212).

[0045] The stator core (1211) is made of a metal material such as electrical steel, and when voltage is applied from the outside to the motor unit (120), it performs electromagnetic interaction through electromagnetic force together with the stator coil (1212) and rotor (122) to be described later.

[0046] The stator core (1211) is formed in a roughly rectangular shape. For example, the inner surface of the stator core (1211) may be formed in a circular shape, and the outer surface may be formed in a rectangular shape. The stator core (1211) may be fixed to the lower surface of the cylinder block (131) described later by a stator fastening bolt (not shown).

[0047] The stator core (1211) can be elastically supported by a support spring (123) on the bottom surface of the shell (110) while being spaced axially and radially apart from the inner surface of the shell (110). Accordingly, vibrations generated during operation can be suppressed from being directly transmitted to the shell (110).

[0048] The stator coil (1212) can be wound inside the stator core (1211). As previously described, when voltage is applied from the outside, the stator coil (1212) generates an electromagnetic force and performs electromagnetic interaction with the stator core (1211) and the rotor (122). Through this, the motor unit (120) generates a driving force for the reciprocating motion of the compression unit (130).

[0049] The rotor (122) may include a rotor core (1221) and a magnet (1222).

[0050] The rotor core (1221), like the stator core (1211), is made of a metal material such as electrical steel and can be formed in a roughly cylindrical shape. A drive shaft (125), which will be described later, can be press-fitted and connected to the center of the rotor core (1221).

[0051] The magnet (1222) is made of a permanent magnet and can be inserted and coupled at equal intervals along the circumferential direction 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 drive shaft (125) rotates together with the rotor (122) and transmits the rotational force of the motor unit (120) to the compression unit (130) through the connecting rod (126).

[0052] 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 by 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).

[0053] 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) may be connected to the stator (121) by a stator-fastening bolt (not shown) and elastically supported on the lower shell (111) together with the stator (121) of the electric motor (120).

[0054] The cylinder block (131) according to the present embodiment may include a frame part (1311), a fixed protrusion (1312) coupled to a stator (121) of a transmission part (120), a bearing part (1313) supporting a drive shaft (125), and a cylinder part (hereinafter abbreviated as cylinder) (1315) forming a compression chamber (130a).

[0055] The frame portion (1311) may be formed in a flat plate shape extending in the transverse direction, or may be formed in a radial plate shape by reducing the thickness of a portion of the edge excluding the corners.

[0056] A fixed protrusion (1312) may be formed on 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 motor portion (120). A fastening hole (1312a) may be formed in the fixed protrusion (1312) to allow a fixed fastening bolt (not shown) and a rear damper (152) to be coupled thereto.

[0057] The bearing portion (1313) may be formed by extending axially in both directions from the central part of the frame portion (1311). A bearing hole (1313a) is formed axially through the bearing portion (1313) so that the drive shaft (125) passes through it, and a bushing bearing may be inserted and coupled to the inner surface of the bearing hole (1313a).

[0058] A drive shaft (125) may be axially supported at the upper end of the bearing portion (1313), and may be radially supported on the inner surface of the bearing portion (1313). Accordingly, the drive shaft (125) may be supported axially and radially by the cylinder block (131).

[0059] The cylinder (1315) may be formed radially eccentrically at one edge of the frame portion (1311). The cylinder (1315) is radially penetrated, and a piston (132) connected to a connecting rod (126) is inserted into the inner opening, and a valve assembly (141) forming the suction / discharge portion (140) to be described later may be mounted at the outer opening.

[0060] The piston (132) can be formed flat with an open side facing the connecting rod (126) (rear side), while the opposite side facing away from the connecting rod (126) (front side) 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) to be described later.

[0061] Referring to FIGS. 1 and 2, the suction and discharge unit (140) according to the present embodiment may include a valve assembly (141), a muffler assembly (142), and a clamping member (143).

[0062] The valve assembly (141) may include an intake valve section (not shown) and a discharge valve section (not shown). The intake valve section may connect the compression chamber (130a) to the intake connection groove (not shown) of the connecting muffler (not shown) to be described later, and the discharge valve section may connect the compression chamber (130a) to the discharge connection groove (not shown) of the connecting muffler (not shown) to be described later. Accordingly, the intake valve section and the discharge valve section may be formed to be adjacent to each other on a plane.

[0063] The muffler assembly (142) may include an intake muffler (142a) and a discharge muffler (142b). In other words, the muffler assembly (142) may have an upper muffler and a lower muffler combined to form an intake space (S1) of the intake muffler (142a) and a discharge space (S2) of the discharge muffler (142b), respectively.

[0064] A discharge protrusion (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 protrusion. In other words, a loop pipe (118) that guides the refrigerant of the discharge space (S2) to the discharge pipe (116) is connected between the discharge protrusion of the discharge muffler (142b) and the discharge pipe (116).

[0065] 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, which has a lower rigidity than that of the loop pipe (118). Accordingly, the damper member (160) can absorb and reduce the vibration of the loop pipe (118) as it deforms due to the vibration of the loop pipe (118). The damper member (160) will be explained again later together with the loop pipe (118).

[0066] The clamping member (143) is provided at the front of the suction / discharge section (140), that is, on the front surface of the muffler assembly (142), so as to fix the muffler assembly (142) to the cylinder block (131) of the compression section (130).

[0067] The damping section (150) is provided on the upper side of the compression section (130) and the suction / discharge section (140). The damping section (150) may include a front damper (151) and a rear damper (152) provided on each side 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 cushion the impact caused by collision between the compression section (130) and the suction / discharge section (140) and the shell (110) when the compressor is driven. The rear damper (152) can effectively suppress or cushion the impact caused by collision between the shell (110) and the compression section (130) when the compressor is driven.

[0068] In the drawing, the unexplained symbols 1251, 1255, and 127 are oil passages, oil feeders, and balance weights, respectively.

[0069] The reciprocating compressor according to the present embodiment as described above operates as follows.

[0070] That is, when power is applied to the electric motor (120), the rotor (122) rotates. When the rotor (122) rotates, the drive shaft (125) connected to the rotor (122) rotates and transmits rotational force to the piston (132) through the connecting rod (126). The piston (132) reciprocates in the forward and backward directions relative to the cylinder (1315) by means of the connecting rod (126).

[0071] For example, when the piston (132) moves backward (intake 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 intake space (S1) of the muffler assembly (142) through the intake pipe (115) passes through the intake valve part of the valve assembly (141) and is sucked into the compression chamber (130a).

[0072] Conversely, when the piston (132) advances (discharge stroke) in the cylinder (1315), the volume of the compression chamber (130a) decreases. When the volume of the compression chamber (130a) decreases, the refrigerant filled in the compression chamber (130a) is compressed and discharged through the discharge valve portion of the valve assembly (141) to the discharge connection groove of the connecting muffler. This refrigerant is then discharged into the discharge space (S2) forming the discharge muffler (142b), and then through the loop pipe (118) and discharge pipe (116) to be discharged into the refrigeration cycle, repeating this series of processes.

[0073] Typically, in the case of a reciprocating compressor, since the loop pipe (118) connects the discharge muffler (142b) and the discharge pipe (116) of the compression section (130), vibrations generated in the compression section (130) during operation of the compressor can be transmitted to the outside of the compressor through the loop pipe (118). Considering this, conventional technologies have been proposed to dampen vibrations in the loop pipe by wrapping a steel spring around a steel loop pipe, applying a plastic loop pipe, or using multiple vibration-reducing sleeves, as previously explained. However, as previously explained, these conventional vibration damping technologies each have their own limitations.

[0074] 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 larger than the outer diameter (D1) of the loop pipe (118) so that when the loop pipe (118) vibrates, the damper member (160) deforms radially and absorbs the vibration.

[0075] 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 illustrating an example in which a damper member is installed in the first straight section of a loop pipe.

[0076] Referring to FIGS. 3 to 5, the loop pipe (118) according to the present embodiment connects the discharge muffler (142b) and the discharge pipe (116) as described above, but can be extended so that at least a portion is submerged in the oil stored in the internal space (110a) of the shell (110).

[0077] For example, the loop pipe (118) may be made of steel or a synthetic resin material such as plastic. This embodiment is described with an example in which the loop pipe (118) is made of steel. Accordingly, the material cost for the loop pipe (118) can be lowered, and the manufacturing cost can be reduced due to the ease of welding.

[0078] Specifically, the loop pipe (118) may be formed in 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 bending it several times along the inner surface of the shell (110). Accordingly, the loop pipe (118) can be extended as long as possible to minimize vibrations transmitted from the compression section (130).

[0079] Additionally, the outer diameter (D1) between the two ends of the loop pipe (118) may be formed to be 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 the assembly and / or behavioral stability of the damper member (160) described later can also be increased.

[0080] 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 transmission of vibrations generated in the compression portion (130) to the discharge pipe (116) through the loop pipe (118).

[0081] For example, the damper member (160) according to the present embodiment may be provided to wrap around the longest first straight section (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 section (118a) of the loop pipe (118) and can effectively dampen vibrations transmitted through the loop pipe (118).

[0082] In this case, the damper member (160) may be formed of a material having a stiffness less 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).

[0083] Additionally, the damper member (160) may be formed in the shape of a smooth tube with a circular inner surface. In other words, the loop pipe (118) may be formed in a circular cross-sectional shape, and the damper member (160) may be formed in a circular cross-sectional shape similar to that of the loop pipe (118). Accordingly, the manufacturing and / or assembly of the damper member (160) may be easy.

[0084] Although not illustrated in the drawing, the inner surface of the damper member (160) is formed smoothly, but may also be formed in other shapes such as an elliptical cross-section, a triangular cross-section, or a square cross-section. In these cases, the outer diameter (D1) of the damper member (160) can be minimized, and an empty space filled with oil can be formed between the inner surface of the damper member (160) and the outer surface of the loop pipe (118) to increase the damping effect.

[0085] Additionally, 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 be suspended and wrapped around the outer surface of the loop pipe (118). Accordingly, when the loop pipe (118) vibrates, the damper member (160) can attenuate the vibration of the loop pipe (118) by vibrating radially with the loop pipe (118) as the center point.

[0086] In this case, since an impact occurs as 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 for the damper member (160) to be formed 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).

[0087] In addition, in this case, the loop pipe (118) may be provided with a stopper (170) to restrict the movement of the damper member (160) in the longitudinal direction of the loop pipe (118). In other words, as 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 as the damper member (160) collides with surrounding parts including the loop pipe (118) and / or the shell (110). Accordingly, stoppers (170) that restrict the longitudinal movement of the damper member (160) may be provided on both sides of the longitudinal direction 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.

[0088] For example, the stopper (170) may be formed as a snap ring as shown in FIG. 5. In this case, a pair of stoppers (170) located on both longitudinal sides relative to the damper member (160) may be snap-fitted and coupled to the loop pipe (118) on both sides of the damper member (160). Accordingly, the longitudinal movement of the damper member (160) can be reliably restricted while easily assembling the stopper (170).

[0089] In a reciprocating compressor as described above, vibrations generated during the operation of the compressor may be transmitted to the discharge pipe (116) through the loop pipe (118), thereby causing compressor vibrations. However, as in the present embodiment, a damper member (160) is provided in the middle of the loop pipe (118), that is, in the first straight section (118a) of the loop pipe (118), so that the damper member (160) can absorb and cancel out the vibrations transmitted to the loop pipe (118). Through this, vibrations generated on the discharge side of the compression section (130) are 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.

[0090] 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) as it deforms according to the vibration of the loop pipe (118).

[0091] In addition, as in the present embodiment, when 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) vibrates within the range indicated by the dotted line in FIG. 4, and due to this vibration, the damper member (160) undergoes greater elastic deformation, thereby further enhancing the vibration reduction effect.

[0092] FIGS. 6 and 7 are graphs comparing the vibration reduction effect of a reciprocating compressor equipped with a damper member according to the present invention with that of a conventional compressor without a damper member and a compressor equipped with a damper member made of a steel spring, respectively. FIGS. 6 is a graph showing the vibration in the operating range of the reciprocating compressor, and FIGS. 7 is a graph showing the vibration in the entire range.

[0093] Referring to FIG. 6, it can be seen that when a damper member according to the present embodiment is provided, it exhibits a superior vibration reduction effect compared to the case where a damper member is not provided (conventional ①) in the operating range of the compressor. In the case of a conventional steel spring (conventional ②), it also exhibits a superior vibration reduction effect compared to the case where a damper member is not provided in the operating range of the compressor. 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 larger compared to the case where a damper member according to the present embodiment is provided. Through this, it can be seen that inserting a damper member (160), which is made of an elastic material and has an inner diameter (D2) larger than the outer diameter (D1) of the loop pipe (118), so as to be suspended from the loop pipe (118) as in the present embodiment is most advantageous in terms of vibration reduction.

[0094] Referring to FIG. 7, it can be seen that when the damper member (160) according to the present embodiment is provided, the amplitude (magnitude of acceleration, ACC) across 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 a conventional steel spring (conventional ②), it can be seen that in the high-frequency band of approximately 1,000 Hz or higher, it exhibits more severe vibration than the present embodiment and even more severe than the case where there is no damper member. Through this, it can be seen that when the damper member (160) of the present embodiment is inserted into the loop pipe (118), the vibration reduction effect is evenly superior across the entire band, not just the operating range mentioned above.

[0095] Meanwhile, other embodiments of the damper member are as follows.

[0096] That is, in the above-described embodiment, the inner surface of the damper member is formed in the shape of a smooth tube, but in some cases, a damping projection may be formed on the inner surface of the damper member.

[0097] FIG. 8 is a cross-sectional view showing another embodiment of a damper member.

[0098] 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 to hang from 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. Since the basic configuration of the loop pipe (118), the damper member (160), and the stoppers (170) and the resulting effects are identical or nearly similar to those in the previously described embodiment, the description thereof is replaced by the description of the previously described embodiment.

[0099] However, in this embodiment, at least one damping projection (160a) may be formed on the inner surface of the damper member (160). For example, a plurality of damping projections (160a) may be formed along the inner surface of the damper member (160). In this case, the plurality of damping projections (160a) may be formed with the same shape and / or specifications 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) during vibration of the loop pipe (118), a uniform damping force can be secured.

[0100] 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 greater than or equal to the outer diameter (D1) of the loop pipe (118). In the former case, while the damping protrusions (160a) are formed on the inner circumference of the damper member (160), the damper member (160) is not constrained by the loop pipe (118) and can be deformed as much as possible by centrifugal force, thereby increasing the vibration reduction effect. In the latter case, a high damping effect can be obtained when the installation space of the damper member (160) is narrow or during low-speed operation. In this embodiment, an example is illustrated in which the minimum diameter of the virtual circle of the damping protrusions (160a) is formed to be larger than the outer diameter (D1) of the loop pipe (118).

[0101] In addition, in this embodiment, an example is shown in which the damping projection (160a) has an arc cross-sectional shape, but it is not limited thereto. For example, the damping projection (160a) may be formed with a triangular cross-sectional shape or a rhombus cross-sectional shape.

[0102] 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) act as a cushion, thereby reducing the impact between the damper member (160) and the loop pipe (118). Through this, damage to the loop pipe (118) and / or the damper member (160) can be suppressed, thereby increasing reliability.

[0103] In addition, in this case, 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, the weight of the damper member (160) increases, and the vibration reduction capability of the damper member (160) can be further improved.

[0104] Meanwhile, another embodiment of the damper member is as follows.

[0105] That is, in the above-described embodiment, the damper member is formed from a single material, but in some cases, the damper member may be formed from multiple materials.

[0106] FIG. 9 is a cross-sectional view showing another embodiment of a damper member.

[0107] 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 to hang from 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. Since the basic configuration of the loop pipe (118), the damper member (160), and the stoppers (170) and the resulting effects are identical or nearly similar to those in the previously described embodiment, the description thereof is replaced by the description of the previously described embodiment.

[0108] However, the damper member (160) according to the present embodiment may be formed from different materials. For example, the damper member (160) may include a first damping part (161) that surrounds the loop pipe (118) and a second damping part (162) that surrounds the first damping part (161). The first damping part (161) may be formed from an elastic material with less rigidity than the loop pipe (118), and the second damping part (162) may be formed from a material heavier than the first damping part (161). In other words, the first damping part may be formed from a rubber material as in the previously described embodiments, and the second damping part (162) may be formed from a metal material such as steel. Accordingly, the vibration reduction effect can be increased without significantly increasing the outer diameter of the damper member (160).

[0109] In this case, the thickness of the first damping part (161) may be formed to be greater than or equal to the thickness of the second damping part (162). In the former case, the cushioning effect of the damper member (160) can be increased as the thickness of the first damping part (161), which is made of an elastic material, is formed thicker, and in the latter case, the weight of the damper member (160) can be increased as the heavy second damping part (162) is formed relatively thicker. This embodiment illustrates an example in which the thickness of the first damping part (161) is formed thicker than the thickness of the second damping part (162).

[0110] As described above, when the damper member (160) is formed of different materials, such that the inner surface is formed of an elastic material and the outer surface is 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 internal space (110a) of the shell (110) is narrow, such as in a small reciprocating compressor, the damper member (160) can minimize interference with other surrounding parts, thereby increasing the vibration reduction effect and / or reliability.

[0111] Although not illustrated in the drawing, at least one fixing projection (not shown) may be formed on the outer surface of the first damping part (161) and / or the inner surface of the second damping part (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 part (162) and / or the outer surface of the first damping part (161) facing it. In this case, the bonding force between the first damping part (161) and the second damping part (162) can be increased.

[0112] Meanwhile, another embodiment of the damper member is as follows.

[0113] That is, in the above-described embodiment, the damper member is formed in the shape of a single tube, but in some cases, the damper member may be formed in the shape of a coil or a plurality of rings.

[0114] FIGS. 10 and FIGS. 11 are cross-sectional views showing other embodiments of a damper member.

[0115] 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 to hang from 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) may be restricted. Since the basic configuration of the loop pipe (118), the damper member (160), and the stoppers (170) and the resulting effects are identical or nearly similar to those in the previously described embodiment, the description thereof is replaced by the description of the previously described embodiment.

[0116] However, unlike the above-described embodiment in which the damper member (160) according to the present embodiment is in the shape of a tube, it may be formed in the shape of a coil 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).

[0117] As described above, when the damper member (160) is formed in a coil shape, vibrations in directions perpendicular to the longitudinal direction of the loop pipe (118), such as the Y and Z directions, are reduced during the operation of the compressor, and at the same time, vibrations 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) extends and retracts along the longitudinal direction of the loop pipe (118).

[0118] This allows for almost the same effect to be obtained even when the damper member (160) is formed in the shape of multiple rings as in FIG. 11. For example, the damper member (160) may be composed of multiple rings. In this case, the multiple rings forming the damper member (160) may be arranged along the longitudinal direction of the loop pipe (118) such that a small gap is formed between each ring. Accordingly, even when the damper member (160) is formed in the shape of a coil as in the embodiment of FIG. 10, each damper member (160) may be frictionally deformed along the longitudinal direction of the loop pipe (118) during the operation of the compressor. Through this, three-directional vibrations including the longitudinal direction of the loop pipe (118) as well as directions perpendicular to the longitudinal direction of the loop pipe (118) can be reduced.

[0119] Meanwhile, another embodiment of the damper member is as follows.

[0120] That is, in the above-described embodiments, the damper member is provided in a straight section extending in the X direction of the loop pipe, but in some cases, the damper member may be provided in other directions, for example, in a straight section extending in the Y direction and / or Z direction as well as in a straight section extending in the X direction.

[0121] FIG. 12 is a schematic diagram illustrating an example in which a damper member is provided in the first straight section and the second straight section of a loop pipe.

[0122] 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 to hang from 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. Since the basic configuration of the loop pipe (118), the damper member (160), and the stoppers (170) and the resulting effects are identical or nearly similar to those in the previously described embodiments, the description thereof is replaced by the description of the previously described embodiments.

[0123] However, in this embodiment, the damper member (160) may be separated into multiple parts and inserted into the loop pipe (118) in different directions. For example, the loop pipe (118) may include a first straight section (118a) extending in the X direction and a second straight section (118b) extending in the Z direction. In this case, a first damper member (165) may be inserted so as to be suspended from the first straight section (118a), and a second damper member (166) may be inserted so as to be suspended from the second straight section (118b). These first damper member (165) and second damper member (166) may be formed in the same way as the embodiments of FIG. 3 through FIG. 9 described above.

[0124] As described above, when a first damper member (165) is provided in the first straight section (118a) extending in the X direction and a second damper member (166) is provided in the second straight section (118b) extending in the Z direction, a vibration reduction effect can be obtained for three directions of the loop pipe (118).

[0125] 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 directions of vibration of the loop pipe (118), namely X, Y, and Z directions, can be obtained.

[0126] Although not illustrated in the drawing, in some cases, only the second damper member (166) may be installed on the second straight section (118b). In this case, as previously explained, a vibration reduction effect in the X and Z directions can be obtained.

[0127] Additionally, although not shown in the drawing, a damper member (not shown) may also be provided in the Y-direction straight section forming the third straight section (not shown) depending on the case. 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 that the damper member does not slide down excessively.

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

[0129] That is, in the aforementioned embodiments, the damper member is provided in the straight section of the loop pipe, but in some cases, the damper member may also be provided in the curved section.

[0130] FIG. 13 is a schematic diagram illustrating an example in which a damper member is provided in the curved portion of a loop pipe.

[0131] 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 hang from the loop pipe (118).

[0132] 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) may be restricted. Since the basic configuration of these loop pipes (118), damper member (160), and stoppers (170) and the resulting effects are identical or nearly similar to those in the previously described embodiments, the description thereof is replaced by the description of the previously described embodiments.

[0133] However, in this embodiment, the third damper member (167) may be provided on 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).

[0134] As described above, when the third damper member (167) is provided on the curved portion (118c) of the loop pipe (118), all three directions of vibration in the X, Y, and Z directions 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.

[0135] In addition, in this case, the third damper member (167) may be provided only on the curved portion (118c), or it may be formed to be long enough to wrap around the first straight portion (118a) and / or the second straight portion (118b) extending from the curved portion (118c). In the former case, as previously explained, 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.

[0136] Although not illustrated in the drawing, the third damper member (167) provided in the curved section (118c) may be separated from the first damper member (165) provided in the first straight section (118a) and / or the second damper member (166) provided in the second straight section (118b). In this case, the assembly of the damper members (165), (166), and (167) can be easy while increasing the vibration reduction effect. Explanation of the symbols

[0137] 110: Shell 110a: Internal space 111: Lower shell 112: Upper shell 115: Suction pipe 116: Discharge pipe 117: Process pipe 118: Loop pipe 118a: 1st straight line section 118b: 2nd straight line section 118c: Curved section 120: Transmission section 121: Stator 1211: Stator core 1212: Stator coil 122: Rotor 1221: Rotor core 1222: Magnet 123: Support spring 125: Drive shaft 1251: Oil Euro 1255: Oil Feeder 126: Connecting rod 127: Balance weight 130: Compression section 130a: Compression chamber 131: Cylinder block 1311: Frame part 1312: Fixed protrusion 1312a: Fastening hole 1313a: Bearing hole 1315: Cylinder part (cylinder) 132: Piston 140: Suction / Discharge Section 141: Valve assembly 142: Muffler assembly 142a: Intake muffler 142b: Discharge muffler 143: Clamping member 150: Damping part 151: Front damper 152: Rear damper 160: Damper member 160a: Damping projection 161: 1st damping section 162: 2nd damping section 165: First damper member 166: Second damper member 167: Third damper member 170: Stopper D1: Outer diameter of the loop pipe D2: Inner diameter of the damper member D3: Minimum inner diameter of the damping projection S1: Suction space S2: Discharge space

Claims

Claim 1 A compressor comprising: a shell; a compression section provided in the internal space of the shell and compressing a refrigerant; a discharge pipe provided to penetrate the shell; a loop pipe that guides the refrigerant compressed in the compression section to the discharge pipe; a damper member formed of a material having a stiffness smaller than that of the loop pipe and wrapping at least a portion of the loop pipe; and a stopper provided in the loop pipe to restrict the movement of the damper member in the longitudinal direction of the loop pipe, wherein the damper member is formed such that the inner diameter of the damper member is larger than the outer diameter of the loop pipe over the entire section along the longitudinal direction of the damper member. Claim 2 In claim 1, the damper member is a compressor formed of an elastic material. Claim 3 delete Claim 4 In claim 1, the damper member is a compressor formed in the shape of a smooth tube, the inner surface of which is circular or elliptical. Claim 5 In claim 1, the damper member is a compressor having at least one damping projection formed on its inner circumference. Claim 6 A compressor according to claim 5, wherein a plurality of damping protrusions are formed along the inner circumferential surface of the damper member, and the minimum diameter of the virtual circle connecting the plurality of damping protrusions is formed to be larger than the outer diameter of the loop pipe. Claim 7 In claim 1, the damper member is a compressor formed in a tube shape, a coil shape, or a plurality of ring shapes. Claim 8 In claim 1, the damper member comprises a first damping portion surrounding the loop pipe; and a second damping portion surrounding the first damping portion, wherein the second damping portion is formed of a material heavier than the first damping portion. Claim 9 In claim 8, the thickness of the first damping part is formed to be greater than or equal to the thickness of the second damping part. Claim 10 In any one of claims 1, 2, 4 through 9, the loop pipe comprises a straight section and a curved section, and the damper member is a compressor inserted into at least one of the straight section and the curved section of the loop pipe. Claim 11 delete Claim 12 In claim 10, a predetermined amount of oil is stored in the internal space of the shell, and the damper member is configured such that at least a portion of it is submerged in the oil.

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