Reciprocating compressor

Abstract

A reciprocating compressor is disclosed. The reciprocating compressor includes a housing, an electric motor, a compressor section, a crankshaft, and a counterweight. The counterweight may be equipped with a spill guide extending from a fixed portion toward the opposite side of the eccentric mass portion, guiding oil spilled from the oil flow path toward the compressor section. This causes a large amount of oil spilled from the oil flow path to be spilled further toward the cylinder and piston, thus ensuring a smooth supply between the inner circumferential surface of the cylinder and the outer circumferential surface of the piston, thereby improving the compressor's cooling capacity and / or energy efficiency.

Description

Technical Field

[0001] This invention relates to a reciprocating compressor. Background Technology

[0002] A reciprocating compressor draws in, compresses, and discharges refrigerant by reciprocating the piston within a cylinder. Reciprocating compressors can be categorized into continuous reciprocating compressors and vibrating reciprocating compressors based on the piston's driving mechanism.

[0003] A connected reciprocating compressor is a type of compressor in which a piston reciprocates within a cylinder via a crankshaft and connecting rod connected to a rotary motor. A vibratory reciprocating compressor is a type of compressor in which a piston reciprocates within a cylinder via a movable part connected to a reciprocating motor. This invention relates to a connected reciprocating compressor. Hereinafter, a reciprocating compressor can be understood as a connected reciprocating compressor.

[0004] In the case of a reciprocating compressor as described above, oil drawn upwards by the crankshaft is sprayed onto the upper end and / or near the upper end of the crankshaft and supplied between the cylinder and the piston.

[0005] However, as mentioned above, in reciprocating compressors, there is a possibility that oil splattering from the upper end and / or near the upper end of the crankshaft may not be adequately supplied between the cylinder and piston. Especially when the reciprocating compressor is operating at low speeds, the oil splatter distance becomes drastically shorter, potentially leading to insufficient oil reaching the cylinder and piston. Consequently, the cylinder, which generates heat during compression, cannot be adequately cooled, potentially resulting in reduced compression efficiency.

[0006] With this in mind, an additional oil supply device, such as an oil guide cap, can be added to the upper end of the crankshaft. However, adding an additional oil supply device not only increases the cost, but also may reduce the reliability of the oil supply device in case it falls off. Summary of the Invention

[0007] The problem that the invention aims to solve

[0008] The purpose of this invention is to provide a reciprocating compressor that can smoothly supply oil between the cylinder and the piston under both high-speed and low-speed operation.

[0009] Another object of the present invention is to provide a reciprocating compressor that can smoothly supply oil between the cylinder and the piston regardless of the operating speed by increasing the dispersion distance of oil scattered from the crankshaft.

[0010] Another object of the present invention is to provide a reciprocating compressor that can extend the oil dispersion distance without the need for additional components.

[0011] Technical solutions to the problem

[0012] To achieve the objectives of this invention, a reciprocating compressor comprising a housing, an electric motor, a compressor, a crankshaft, and a counterweight can be provided. The housing can store a predetermined amount of oil. The electric motor can be disposed inside the housing, providing driving force. The compressor can use the driving force of the electric motor to cause a piston to reciprocate within a cylinder to compress refrigerant. The crankshaft can be provided with an eccentric portion eccentric relative to a center of rotation, and can be provided with an oil flow path to draw oil stored in the housing upward toward the eccentric portion. The counterweight can be attached to the eccentric portion of the crankshaft and rotates with the crankshaft. The counterweight can include a fixed portion, an eccentric mass portion, and a spill guide portion. The fixed portion can be attached to the eccentric portion of the crankshaft. The eccentric mass portion can extend radially eccentrically from the fixed portion. The spill guide portion can extend from the fixed portion in a direction opposite to the eccentric mass portion, guiding oil spilled from the oil flow path toward the compressor side. As a result, a large amount of oil from the oil flow path is dispersed further towards the cylinder and piston, thus ensuring a smooth supply between the inner circumferential surface of the cylinder and the outer circumferential surface of the piston, thereby improving the compressor's cooling capacity and / or energy efficiency.

[0013] As an example, at least a portion of the scattering guide can be located on an imaginary line passing through the center of gravity of the eccentric mass and the center of the eccentric portion of the crankshaft. Thus, even if the scattering guide extends radially from one side of the circumference of the eccentric mass, the center of gravity of the counterweight is located on the imaginary line, thereby effectively counteracting the eccentric load caused by the eccentric portion of the crankshaft.

[0014] For example, the two sides of the circumferential guide portion can be formed symmetrically with respect to the imaginary line. Thus, even if the scattering guide portion extends radially from one side of the circumferential mass portion, it can effectively counteract the eccentric load caused by the eccentric portion of the crankshaft.

[0015] Alternatively, the oil splatter guide can be asymmetrically shaped with reference to the imaginary line, offset to the opposite side of the crankshaft's rotation direction. This allows for the smooth guidance of a large amount of oil splattered from the oil splatter orifice to the cylinder and piston sides while minimizing the area of ​​the oil splatter guide.

[0016] As another example, the oil spill guide can be formed eccentrically to one side in the circumferential direction relative to an imaginary line passing through the center of gravity of the eccentric mass and the center of the eccentric part of the crankshaft. This allows for the smooth guidance of a large amount of oil spilled from the oil spill hole to the cylinder and piston sides while minimizing the area of ​​the oil spill guide.

[0017] For example, the oil splatter guide can be formed on the opposite side of the crankshaft's rotation direction. Thus, even at high and low speeds, a large amount of oil splattered from the oil splatter holes can be smoothly guided to the cylinder and piston sides while minimizing the area of ​​the oil splatter guide.

[0018] As another example, the scattering guide can be formed with a circumferential length greater than or equal to the radial length. This allows for the smooth guidance of a large amount of oil scattering from the oil scattering hole to the space between the cylinder and piston while minimizing the radial length of the scattering guide.

[0019] As another example, the scattering guide can be formed with a circumferential length less than or equal to the radial length. Therefore, by maximizing the radial length of the scattering guide, the scattering distance can be further increased.

[0020] As another example, the scattering guide can be formed such that the gap between the two circumferential sides narrows as it moves away from the fixed part. This allows for a maximum radial length of the scattering guide while minimizing its area, thus enabling the smooth guidance of a large amount of oil scattering from the oil scattering hole to the space between the cylinder and the piston.

[0021] As another example, the scattering guide can be formed such that at least a portion of the interval between the two circumferential side surfaces is the same in the radial direction. This allows for an increase in the oil scattering distance and / or scattering amount while maintaining a relatively small radial length of the scattering guide.

[0022] As another example, the distance between the center of the eccentric portion and the end of the scattering guide portion can be less than the value of the shortest distance between the end of the cylinder and the eccentric mass portion when the piston is at top dead center, minus the eccentricity of the eccentric portion. This prevents the scattering guide portion of the counterweight from colliding with the cylinder when the counterweight rotates.

[0023] As another example, the crankshaft may have an oil splatter hole extending from the oil flow path and penetrating the outer peripheral surface of the eccentric portion. The circumferential length of the splatter guide portion may be greater than or equal to the inner diameter of the oil splatter hole. Thus, the circumferential length of the splatter guide portion can be appropriately set according to the size of the oil splatter hole, so that the oil splattered from the oil splatter hole can be smoothly guided to the space between the cylinder and the piston.

[0024] As another example, the crankshaft may have an oil splatter hole extending from the oil flow path and penetrating the outer peripheral surface of the eccentric portion. The distance between the upper end of the eccentric portion and the top surface of the splatter guide portion may be greater than or equal to the distance between the upper end of the eccentric portion and the center of the oil splatter hole. This improves the assemblability and / or reliability of the counterweight, and ensures that the splatter guide portion of the counterweight is not too far from the lower end of the oil splatter hole, thereby enabling smooth oil guidance between the cylinder and piston.

[0025] For example, the top surface of the scattering guide can be located at the same height as the lower end of the oil scattering hole. This further increases the oil scattering distance by minimizing the axial drop of oil discharged from the oil scattering hole.

[0026] Furthermore, the top surface of the oil splatter guide can be located lower than the lower end of the oil splatter orifice, and the distance between the lower end of the oil splatter orifice and the top surface of the oil splatter guide can be less than or equal to the inner diameter of the oil splatter orifice. This improves the assemblability and / or reliability of the counterweight, and ensures that the oil splatter guide of the counterweight is not too far from the lower end of the oil splatter orifice, thereby enabling smooth oil guidance between the cylinder and piston.

[0027] As another example, the oil flow path can extend through the upper end of the eccentric portion. The distance between the upper end of the eccentric portion and the top surface of the scattering guide portion can be less than or equal to the inner diameter of the oil flow path at the upper end of the eccentric portion. This facilitates the machining of the crankshaft including the oil flow path while ensuring smooth oil supply between the cylinder and piston.

[0028] As another example, the scattering guide portion can be formed to have the same thickness as the fixing portion. This allows for easy fabrication of the scattering guide portion.

[0029] As another example, the scattering guide can be thinner than the fixed part. This reduces the weight of the scattering guide, allowing for an increase in its circumferential and / or radial length to increase the oil supply between the cylinder and piston.

[0030] As another example, the top surface of the oil scattering guide can be flush with the top surface of the fixing part. This facilitates the machining of the oil scattering guide and allows the oil discharged through the oil scattering hole to scatter further towards the cylinder.

[0031] As another example, the top surface of the scattering guide can be inclined or curved, becoming axially higher as it approaches the outer periphery from the inner periphery of the scattering guide. This further improves the scattering guiding effect while maintaining the same circumferential and / or radial length of the scattering guide.

[0032] As another example, the scattering guide portion can be formed within a range of ±45 degrees in the circumferential direction, with an imaginary line passing through the center of gravity of the eccentric mass portion and the center of the eccentric portion of the crankshaft as a reference. Therefore, by preventing the scattering guide portion from being formed too wide in the circumferential direction, even if a scattering guide portion is formed on the opposite side of the eccentric mass portion, the reduction in the eccentric load offsetting effect of the eccentric mass portion due to the scattering guide portion can be suppressed.

[0033] For example, the scattering guide can be formed in a portion of the range. Thus, while forming the scattering guide, it is possible to suppress the halving of the eccentric load offsetting effect of the eccentric mass due to the scattering guide, and by minimizing the increase in the weight of the counterweight, it is possible to suppress the decrease in motor efficiency.

[0034] Furthermore, the scattering guide can be formed over the entire range of the specified area. Therefore, by maximizing the area of ​​the scattering guide, a large amount of oil scattering from the oil scattering hole can be more smoothly guided between the cylinder and piston.

[0035] In addition, to achieve the objectives of this invention, a reciprocating compressor comprising a housing, an electric motor, a compressor, a crankshaft, and a counterweight can be provided. The housing can store a predetermined amount of oil. The electric motor can be disposed inside the housing, providing driving force. The compressor can use the driving force of the electric motor to cause a piston to reciprocate within a cylinder to compress the refrigerant. The crankshaft can be provided with an eccentric portion offset from the center of rotation, and can be provided with an oil flow path to draw oil stored in the housing upwards toward the eccentric portion. The counterweight can be attached to the eccentric portion of the crankshaft and rotates with the crankshaft. An oil splatter hole can be formed on the outer peripheral surface of the eccentric portion, through which one end of the oil flow path passes. The counterweight can be provided with a fixing portion surrounding and attached to the eccentric portion of the crankshaft. The fixing portion can be attached at a position where the distance between the top surface of the fixing portion and the center of the oil splatter hole is less than or equal to the inner diameter of the oil splatter hole. As a result, the oil discharged through the oil scattering hole spreads further along the fixed part of the counterweight toward the cylinder side, thus enabling a smooth oil supply between the cylinder and the piston.

[0036] As an example, the fixing part is coupled such that its top surface is at the same height as the lower end of the oil splatter hole. Therefore, by minimizing the axial drop of oil discharged from the oil splatter hole, the oil splatter distance can be further increased.

[0037] As another example, the top surface of the fixing part can be formed into the same plane in the radial direction. This facilitates the machining of the fixing part and allows the oil discharged through the oil splatter hole to be guided to splatter further towards the cylinder side.

[0038] As another example, the top surface of the fixing part can be formed such that its axial height increases as it approaches the outer circumferential surface from the inner circumferential surface of the fixing part. This further improves the dispersion guiding effect while maintaining the same radial length of the fixing part.

[0039] As another example, the counterweight may further include a dispersion guide that extends radially from the outer peripheral surface of the fixed part, guiding the oil dispersed from the oil flow path toward the compression section. This causes a large amount of oil discharged through the oil flow path to disperse further toward the cylinder and piston, thereby ensuring a smooth supply between the inner peripheral surface of the cylinder and the outer peripheral surface of the piston, thus improving the compressor's cooling capacity and / or energy efficiency.

[0040] Invention Effects

[0041] The reciprocating compressor of the present invention may include a housing, an electric motor, a compressor section, a crankshaft, and a counterweight. The counterweight may be provided with a spill guide, which extends from the fixed part in the direction opposite to the eccentric mass section, and guides the oil spilled from the oil flow path toward the compressor section. As a result, a large amount of oil spilled from the oil flow path is spilled further toward the cylinder and piston, thereby smoothly supplying the oil between the inner circumferential surface of the cylinder and the outer circumferential surface of the piston, thereby improving the compressor's cooling capacity and / or energy efficiency.

[0042] In the reciprocating compressor of the present invention, at least a portion of the scattering guide portion can be located on an imaginary line passing through the center of gravity of the eccentric mass portion and the center of the eccentric portion of the crankshaft. Thus, even if the scattering guide portion extends radially from one side of the circumferential direction of the eccentric mass portion, the center of gravity of the counterweight is located on the imaginary line, thereby effectively counteracting the eccentric load caused by the eccentric portion of the crankshaft.

[0043] In the reciprocating compressor of the present invention, the oil spill guide can be eccentrically positioned relative to an imaginary line passing through the center of gravity of the eccentric mass and the center of the eccentric portion of the crankshaft, and spaced to one side in the circumferential direction. This allows for the smooth guidance of a large amount of oil spilled from the oil spill guide to the cylinder and piston sides while minimizing the area of ​​the oil spill guide.

[0044] In the reciprocating compressor of the present invention, the top surface of the oil scattering guide can be made to the same plane as the top surface of the fixed part. This facilitates the machining of the oil scattering guide and allows the oil discharged through the oil scattering hole to scatter further toward the cylinder side.

[0045] In the reciprocating compressor of the present invention, the top surface of the scattering guide can be inclined or curved, such that it becomes axially higher as it approaches the outer circumference from the inner circumference of the scattering guide. This further improves the scattering guiding effect while maintaining the same circumferential and / or radial length of the scattering guide.

[0046] In the reciprocating compressor of the present invention, the scattering guide portion can be formed on both sides in the circumferential direction within a range of ±45 degrees, with an imaginary line passing through the center of gravity of the eccentric mass portion and the center of the eccentric portion of the crankshaft as a reference. Therefore, by preventing the scattering guide portion from being formed too wide in the circumferential direction, even if a scattering guide portion is formed on the opposite side of the eccentric mass portion, the reduction in the eccentric load offsetting effect of the eccentric mass portion due to the scattering guide portion can be suppressed.

[0047] The reciprocating compressor of the present invention may include a housing, an electric motor, a compression unit, a crankshaft, and a counterweight. The fixing part of the counterweight may be coupled at a position where the distance between the top surface of the fixing part and the center of the oil splatter hole is less than or equal to the inner diameter of the oil splatter hole. Thus, oil discharged through the oil splatter hole is dispersed further towards the cylinder side along the fixing part of the counterweight, thereby enabling a smooth oil supply between the cylinder and the piston. Attached Figure Description

[0048] Figure 1 This is a perspective view showing the interior of the reciprocating compressor housing of this embodiment, disassembled.

[0049] Figure 2 It is shown Figure 1 A cross-sectional view of the interior of a reciprocating compressor.

[0050] Figure 3 This is a perspective view showing the balance weights of this embodiment disassembled from the crankshaft.

[0051] Figure 4 It is Figure 3 The balancing counterweights are assembled onto the crankshaft and shown in a three-dimensional diagram.

[0052] Figure 5 yes Figure 4 Top view.

[0053] Figure 6 yes Figure 5 The sectional view along line "VI-VI".

[0054] Figure 7 This is a top view showing the balancing weight provided with the scattering guide of this embodiment.

[0055] Figure 8a and Figure 8b This is a schematic diagram simulating the scattering distance at different operating speeds with and without a scattering guide.

[0056] Figure 9a and Figure 9b It is a graph comparing the cooling force and energy efficiency at different operating speeds with and without a scattering guide.

[0057] Figure 10 This is a top view showing a balancing counterweight with a scattering guide provided in another embodiment.

[0058] Figure 11 This is a top view showing a balancing counterweight with a scattering guide provided in another embodiment.

[0059] Figure 12 This is a top view showing a balancing counterweight with a scattering guide provided in another embodiment.

[0060] Figure 13 and Figure 14 This is a top view showing a balancing counterweight with a scattering guide provided in another embodiment.

[0061] Figure 15 This is a cross-sectional view showing a balancing counterweight with a scattering guide in another embodiment.

[0062] Figure 16 This is a cross-sectional view showing the assembly position of the balancing weight for this embodiment.

[0063] Figure 17 This is a cross-sectional view showing the assembly position of the balancing weight for this embodiment. Detailed Implementation

[0064] The reciprocating compressor of the present invention will now be described in detail based on an embodiment shown in the accompanying drawings. In this specification, even in different embodiments, the same or similar reference numerals are used for the same or similar constituent elements, and the first description is used instead of the subsequent description.

[0065] Unless otherwise expressly stated in the context, the singular expressions used in this specification may also include plural expressions. Furthermore, in describing the embodiments disclosed in this specification, detailed descriptions of related well-known technologies are omitted if they are deemed to obscure the essence of the embodiments disclosed herein.

[0066] Additionally, it should be noted that the accompanying drawings are only for the purpose of facilitating the understanding of the embodiments disclosed in this specification, and should not be construed as limiting the technical concepts disclosed in this specification to the drawings.

[0067] In addition, in the following description, with the piston as the reference, the compression chamber side is defined as the front and the opposite side is defined as the rear. With the crankshaft axis as the reference, the lower housing side is defined as the axial lower side and the upper housing side is defined as the axial upper side.

[0068] Figure 1 This is a perspective view showing the interior of the reciprocating compressor housing as described in this embodiment. Figure 2 It is shown Figure 1A cross-sectional view of the interior of a reciprocating compressor.

[0069] Reference Figure 1 and Figure 2 The reciprocating compressor of this embodiment may include a housing 110 forming the exterior, an electric motor 120 disposed in the internal space 110a of the housing 110 and providing driving force, a compression unit 130 receiving driving force from the electric motor 120 to compress refrigerant, and an intake and discharge unit 140 guiding refrigerant to the compression chamber 130a and discharging the compressed refrigerant.

[0070] The housing 110 may include a lower housing 111 and an upper housing 112. The lower housing 111 and the upper housing 112 may be combined to form a sealed internal space 110a. The internal space 110a of the housing 110 may accommodate the electric motor 120 and the compression motor 130. The housing 110 may be made of a lightweight aluminum alloy (hereinafter simply referred to as aluminum) with high thermal conductivity.

[0071] The lower outer shell 111 can be formed into a generally hemispherical shape. A suction pipe 115, a discharge pipe 116, and a process pipe (not shown) can be respectively connected through the lower outer shell 111. These suction pipes 115, discharge pipes 116, and process pipes can be connected to the lower outer shell 111 by insert die casting process.

[0072] The upper outer shell 112 can be formed in a generally hemispherical shape, like the lower outer shell 111. The upper outer shell 112 can be joined to the lower outer shell 111 on the upper side to form the aforementioned internal space 110a of the outer shell 110.

[0073] Reference Figure 1 and Figure 2 In this embodiment, the electric unit (or drive motor) 120 may include a stator 121 and a rotor 122. The stator 121 may be elastically supported on the inner space 110a of the outer casing 110, that is, the bottom surface of the lower outer casing 111, and the rotor 122 may be rotatably disposed on the inner side of the stator 121.

[0074] The stator 121 may include a stator core 1211 and a stator coil 1212.

[0075] The stator core 1211 is made of metal materials such as electrical steel plate. If a voltage is applied to the electric motor 120 from the outside, the stator core 1211, together with the stator coil 1212 and the rotor 122 described later, performs electromagnetic interaction caused by electromagnetic force.

[0076] The stator core 1211 is formed in a generally quadrilateral cylindrical shape. For example, the inner circumferential surface of the stator core 1211 can be formed as a circle, while its outer circumferential surface can be formed as a quadrilateral shape. The stator core 1211 can be fixed to the bottom surface of the cylinder block 131 described later using stator fastening bolts (not shown).

[0077] With the stator core 1211 and the inner surface of the housing 110 separated axially and radially, the lower end of the stator core 1211 can be elastically supported on the bottom surface of the housing 110 by a support spring 123. This can suppress the direct transmission of vibrations generated during operation to the housing 110.

[0078] The stator coil 1212 can be wound inside the stator core 1211. As described above, if a voltage is received 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. As a result, the electric motor 120 generates a driving force for reciprocating the compression unit 130.

[0079] The rotor 122 may include a rotor core 1221 and a magnet 1222.

[0080] Similar to the stator core 1211, the rotor core 1221 can be made of metal materials such as electrical steel sheet and can be formed into a generally cylindrical shape. A crankshaft 125, which will be described later, can be pressed into the center of the rotor core 1221.

[0081] Magnets 1222 can be formed of permanent magnets and can be inserted into rotor core 1221 at equal intervals along the circumferential direction of rotor core 1221. When voltage is applied, rotor 122 rotates through electromagnetic interaction with stator core 1211 and stator coils 1212. As a result, crankshaft 125, while rotating together with rotor 122, transmits the rotational force of electric motor 120 to compression unit 130 via connecting rod 126.

[0082] The crankshaft 125 in this embodiment may include a shaft portion 1251, a supported portion 1252, a plate portion 1253, and an eccentric portion 1254.

[0083] The shaft portion 1251 is pressed into the rotor core 1221. A first oil flow path 1255a, forming part of the oil flow path 1255, can be formed inside the shaft portion 1251. The first oil flow path 1255a extends through the lower end of the shaft portion 1251, and an oil supply device 1256 can be provided at the lower end of the first oil flow path 1255a. Thus, the oil supply device 1256 can pump oil stored in the lower half of the housing 110 while rotating with the shaft portion 1251. This oil can be guided via the first oil flow path 1255a to the second oil flow path 1255b provided on the outer peripheral surface of the supported portion 1252.

[0084] The supported part 1252 is located in the middle of the crankshaft 125, that is, between the shaft part 1251 and the eccentric part 1254, and is a part that can be rotatably inserted into the bearing part 1313 of the cylinder block 131 described later.

[0085] The plate portion 1253 extends radially in a flange shape at the upper end of the supported portion 1252 and is rotatably supported on the upper end face of the bearing portion 1313 of the cylinder block 310 (described later). A bearing component such as a ball bearing (not shown) can be provided between the plate portion 1253 and the bearing portion 1313 facing it. Thus, the crankshaft 125 can be axially supported by the cylinder block 131.

[0086] An eccentric portion 1254 may be formed extending axially from the top surface of the plate portion 1253. The eccentric portion 1254 is formed eccentrically relative to the rotation center (or the rotation center of the shaft portion) Oc of the crankshaft 125, and the connecting rod 126, described later, can be rotatably fitted into the eccentric portion 1254. Thus, when the crankshaft 125 rotates, the connecting rod 126 reciprocates linearly in the front-rear direction, converting the rotational motion of the crankshaft 125 into the linear reciprocating motion of the piston 132.

[0087] Furthermore, a third oil flow path 1255c is formed inside the eccentric portion 1254, which communicates with the second oil flow path 1255b and constitutes another part of the oil flow path 1255. The third oil flow path 1255c passes through the upper end of the eccentric portion 1254. An oil scattering hole 1255d, which constitutes the outlet of the oil flow path 1255, can be formed at the middle height of the eccentric portion 1254. The oil scattering hole 1255d extends radially to the outer peripheral surface of the eccentric portion 1254. As a result, the oil drawn upward into the eccentric portion 1254 is scattered from the third oil flow path 1255c and / or the oil scattering hole 1255d, thereby cooling the electric motor 120 and the compressor 130 while lubricating the cylinder 1314 and piston 132 constituting the compressor 130.

[0088] Furthermore, a counterweight 127 to counteract eccentric loads can be incorporated into the eccentric portion 1254. For example, the counterweight 127 can be pressed into the outer peripheral surface of the eccentric portion 1254 and integrally integrated. Thus, the counterweight 127 and the eccentric portion 1254 rotate together in an eccentric state relative to the rotation center Oc of the crankshaft 125 to counteract eccentric loads. The counterweight 127 will be described further later.

[0089] Reference Figure 1 and Figure 2 In this embodiment, the compression section 130 may include a cylinder block 131 and a piston 132. The cylinder block 131 is elastically supported on the housing 110, and the piston 132 is connected to the crankshaft 125 via a connecting rod 126 and moves relative to the cylinder block 131.

[0090] The cylinder block 131 can be disposed on one axial side of the electric motor 120, such as the upper side. The cylinder block 131 can be fastened to the stator 121 by means of stator fastening bolts (not shown), and can be elastically supported together with the stator 121 of the electric motor 120 on the lower housing 111.

[0091] The cylinder block 131 may include a frame portion 1311, a fixing protrusion 1312, a bearing portion 1313, and a cylinder portion (hereinafter simply referred to as cylinder) 1314. The frame portion 1311 is the part that constitutes the body of the cylinder block 131, the fixing protrusion 1312 is the part that is connected to the stator 121 of the electric unit 120, the bearing portion 1313 is the part that supports the crankshaft 125, and the cylinder 1314 is the part in which the piston 132 is slidably inserted to form a compression space V.

[0092] The frame portion 1311 can be formed into a laterally extending flat plate shape, or a portion of its edge (excluding the corners) can be processed to reduce weight and form a radial plate shape. Thus, the frame portion 1311 is disposed above the electric motor portion 120, thereby allowing the electric motor portion 120 and the compression portion 130 to be separated.

[0093] A fixing protrusion 1312 may be formed on the edge of the frame portion 1311. For example, the fixing protrusion 1312 may be formed by protruding downward from the edge of the frame portion 1311 toward the electric motor portion 120. As a result, the cylinder block 131 may be bolted to the stator 121 and may be elastically supported together with the stator 121 of the electric motor portion 120 on the lower housing 111.

[0094] The bearing portion 1313 can be formed by extending axially to both sides from the center portion of the frame portion 1311. A bearing hole 1313a can be formed through the bearing portion 1313 axially so that the crankshaft 125 can pass through. Thus, the shaft portion 1251 of the crankshaft 125 can be inserted into the bearing portion 1313 and radially supported, and the plate portion 1253 of the crankshaft 125 can be placed on the upper end of the bearing portion 1313 and axially supported.

[0095] The cylinder 1314 can be formed radially eccentrically on one side edge of the frame portion 1311. The cylinder 1314 can be radially penetrated, with a piston 132 connected to the connecting rod 126 inserted into the inner open end, and a valve assembly 141 constituting the intake and exhaust portion 140 described later mounted on the outer open end. Thus, the piston 132 can be inserted linearly and reciprocally inside the cylinder 1314, thereby forming a compression chamber 130a.

[0096] In this embodiment, the piston 132 can have an opening on the side facing the connecting rod 126 (rear side), while its opposite side, i.e., the front side facing away from the connecting rod 126, can be formed into a blocked shape. Thus, the connecting rod 126 can be inserted into the rear side of the piston 132 and rotatably engaged, and the front side of the piston 132, being formed into a blocked shape, can form a compression chamber 130a inside the cylinder 1314 together with the valve assembly 141 described later.

[0097] Furthermore, the piston 132 can be formed of the same material as the cylinder block 131, such as an aluminum alloy. As a result, the transmission of magnetic flux from the rotor 122 to the piston 132 can be suppressed, and since the cylinder block (specifically, the cylinder) 131 and the piston 132 have the same coefficient of thermal expansion, interference between the cylinder block 131 and the piston 132 caused by thermal expansion can be suppressed.

[0098] The intake and discharge section 140 of this embodiment may include a valve assembly 141, an intake muffler 142, and an discharge muffler 143. The valve assembly 141 is a component for opening and closing the compression chamber 130a of the cylinder block 131, the intake muffler 142 is a component for reducing the intake noise of refrigerant drawn into the compression chamber 130a, and the discharge muffler 143 is a component for reducing the discharge noise of refrigerant discharged from the compression chamber 130a.

[0099] Valve assembly 141 may have an intake valve (not shown) and an exhaust valve (not shown) and be attached to the end of cylinder block 131. The intake valve and exhaust valve may be provided separately, but they can also typically be formed together on the same valve plate. The intake valve may be configured to open and close in the direction of piston 132, while the exhaust valve may be configured to open and close in the opposite direction to the intake valve. Thus, no additional retainer is provided for the intake valve, but a retainer may be provided for the exhaust valve to limit its opening.

[0100] The intake muffler 142 may be provided with an intake space in which the inlet is indirectly connected to the intake pipe 115, and the outlet of the intake space may be directly connected to the intake side of the valve assembly 141. Thus, the refrigerant can be drawn into the compression chamber 130a of the cylinder 1314 in a state where the intake noise is attenuated when passing through the intake space of the intake muffler 142.

[0101] The discharge silencer 143 may be provided with a discharge space portion whose inlet is connected to the discharge side of the valve assembly 141, and the outlet of the discharge space portion may be directly connected to the discharge pipe 116 via the annular pipe 117. Thus, a low-pressure compressor can be formed in which the refrigerant compressed in the compression chamber 130a can be directly discharged to the outside of the compressor via the annular pipe 118 and the discharge pipe 116 without passing through the internal space 110a of the outer casing 110.

[0102] The reciprocating compressor of this embodiment, as described above, operates in the following manner.

[0103] That is, if power is applied to the electric motor 120, the rotor 122 rotates. As the rotor 122 rotates, the crankshaft 125 coupled to the rotor 122 rotates, and the rotational force is transmitted to the piston 132 via the connecting rod 126. The piston 132 reciprocates relative to the cylinder 1314 in the front-rear direction via the connecting rod 126.

[0104] For example, if the piston 132 retracts in the cylinder 1314 (intake stroke), the volume of the compression chamber 130a increases, so that the refrigerant is drawn into the compression chamber 130a through the intake pipe 115 and the intake muffler 142. If the piston 132 advances in the cylinder 1314 (exhaust stroke), the volume of the compression chamber 130a decreases, so that the refrigerant filled in the compression chamber 130a is compressed and discharged into the refrigeration cycle through the exhaust muffler 143, the annular pipe 118 and the exhaust pipe 116, and the above series of processes are repeated.

[0105] At this time, the oil stored in the internal space 110a of the outer casing 110 is drawn upward along the first oil flow path 1255a of the crankshaft 125, and is dispersed through the third oil flow path 1255c which opens to the upper half of the crankshaft 125, that is, the upper end of the eccentric portion 1254, and / or the oil scattering hole 1255d which opens to the outer peripheral surface of the eccentric portion 1254. Part of the oil cools the electric motor 120, while the other part of the oil is supplied between the inner peripheral surface of the cylinder 1314 that constitutes the compression section 130 and the outer peripheral surface of the piston 132, thereby cooling and / or lubricating the cylinder 1314 and the piston 132.

[0106] However, in the prior art, the oil scattering from the third oil flow path 1255c and / or the oil scattering hole 1255d cannot smoothly reach the cylinder 1314 and / or the piston 132. Therefore, frictional losses due to insufficient oil and / or refrigerant leakage may occur between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132, resulting in a reduction in cooling capacity. This situation may become more pronounced when the compression volume increases and the contact area between the cylinder 1314 and the piston 132 increases.

[0107] Therefore, in this embodiment, a scattering guide 1273 extending towards the cylinder 1314 can be formed on the balance weight 127, or the balance weight 127 can be arranged adjacent to the oil scattering hole 1255d without forming an additional scattering guide on the balance weight 127. Thus, a large amount of oil scattering from the oil scattering hole 1255d is scattered further away from the oil scattering hole 1255d towards the cylinder 1314 and piston 132, thereby ensuring a smooth supply between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132.

[0108] Figure 3 This is a perspective view showing the balance weights of this embodiment disassembled from the crankshaft. Figure 4 It is Figure 3 A three-dimensional view showing the balancing counterweights assembled onto the crankshaft. Figure 5 yes Figure 4 Top view, Figure 6 yes Figure 5 Sectional view along line "VI-VI", Figure 7 This is a top view showing the balancing weight provided with the scattering guide of this embodiment.

[0109] Reference Figures 3 to 5 The counterweight 127 in this embodiment may include a fixing part 1271, an eccentric mass part 1272, and a spill guide part 1273. The fixing part 1271 is the part that is connected to the crankshaft 125, the eccentric mass part 1272 is the part that counteracts the eccentric load generated by the eccentric part 1254 of the crankshaft 125, and the spill guide part 1273 is the part that disperses a large amount of oil from the oil spill hole 1255d of the crankshaft 125 to a more distant position towards the cylinder 1314 and the piston 132.

[0110] The fixing part 1271 can be formed as a ring. For example, the fixing part 1271 can be formed with a fixing hole 1271a through its center. Thus, the fixing part 1271 can be fitted into and fixed to the eccentric part 1254 of the crankshaft 125.

[0111] In this case, the fixing portion 1271 can be formed with the same or approximately the same thickness and width in the circumferential direction. Therefore, the fixing portion 1271 exerts the same or approximately the same binding force in the circumferential direction, thereby ensuring that the counterweight 127 can be stably attached to the crankshaft 125. This embodiment shows an example where the radial width of the fixing portion 1271 is formed to be approximately the same. In other words, in this embodiment, the radial width of the fixing portion 1271 on the opposite side of the eccentric mass portion 1272 can be formed to be narrower. However, in the following description, it can be defined as the fixing portion 1271 having the same radial width.

[0112] Although not shown, the fixing portion 1271 may also be formed with different widths and thicknesses along the circumferential direction. For example, the width and / or thickness of the side of the fixing portion 1271 away from the eccentric mass portion 1272 may be relatively smaller than the width and / or thickness of the side of the fixing portion 1271 closer to the eccentric mass portion 1272. In this case, the fixing portion 1271 may form part of the eccentric mass portion 1272 together with it. Conversely, it may also be formed in the opposite way to improve the reliability of the fixing portion 1271.

[0113] Furthermore, in this case, at least one or more fixing protrusions 1271c can be formed on the inner circumferential surface of the fixing portion 1271. For example, on the inner circumferential surface of the fixing hole 1271a, a plurality of fixing protrusions 1271c can be formed by protruding radially. Therefore, the radial width of the fixing portion 1271, including the fixing protrusions 1271c, can be formed differently along the circumferential direction. In other words, the radial width of the fixing portion 1271 can be wider in the portion where the fixing protrusions 1271c are provided, and narrower in the portion where the fixing protrusions 1271c are not provided. However, it can be understood below that the radial width of the fixing portion 1271 is defined as the width excluding the fixing protrusions 1271c.

[0114] Reference Figure 6 In this embodiment, the fixing part 1271 can be attached to the lower side of the oil scattering hole 1255d. For example, the fixing part 1271 can be attached to the eccentric part 1254 such that the top surface 1271b of the fixing part 1271 facing away from the electric motor 120 is lower than the lower end of the oil scattering hole 1255d. For example, the top surface 1271b of the fixing part 1271 and the lower end P2 of the oil scattering hole 1255d are located on the same line in the radial direction. In other words, the fixing part 1271 can be attached to the eccentric part 1254 such that the top surface 1273a of the scattering guide part 1273 and the lower end P2 of the oil scattering hole 1255d are located at the same height. As a result, the fixing part 1271 will not overlap with the oil scattering hole 1255d in the radial direction, so that the oil drawn upward through the oil flow path 1255 can be smoothly scattered through the oil scattering hole 1255d.

[0115] The eccentric mass portion 1272 can extend radially from the outer peripheral surface of the fixed portion 1271. For example, the eccentric mass portion 1272 can be formed eccentrically relative to the fixed portion 1271 with reference to the rotation center Oc of the crankshaft 125; in other words, it can be formed eccentrically in the opposite direction to the eccentric portion 1254. Thus, the eccentric mass portion 1272 can generate an eccentric load through centrifugal force when the crankshaft 125 rotates, counteracting the eccentric load generated by the eccentric portion 1254 of the crankshaft 125.

[0116] The eccentric mass portion 1272 can be formed in a semi-circular shape and can be thicker than the fixing portion 1271. For example, the eccentric mass portion 1272 can be formed by forging, or by welding or fastening a plurality of mass portions into a block, or by folding and bending a plurality of mass portions. In the former case, the reliability of the eccentric mass portion 1272 can be improved, while in the latter case, the weight of the eccentric mass portion 1272 can be easily adjusted. This embodiment will be described using the former as an example.

[0117] Reference Figures 5 to 7In this embodiment, the scattering guide 1273 can extend radially from the outer peripheral surface of the fixing part 1271 on the other side. For example, the scattering guide 1273 can be formed from a position higher than the highest point of the piston 132, extending toward the piston 132 in a direction opposite to the eccentric mass part 1272. As a result, in the oil scattering through the oil scattering hole 1255d, a large amount of oil is scattered further along the scattering guide 1273, thereby increasing the amount of oil supplied between the cylinder 1314 and the piston 132.

[0118] Specifically, in this embodiment, the scattering guide 1273 can be configured not to be higher than the oil scattering hole 1255d. In other words, the scattering guide 1273 can be formed at a position where the distance G1 between the top surface 1273a of the scattering guide 1273 and the upper end 1254a of the eccentric portion 1254 is greater than or equal to the distance G2 between the center Oh of the oil scattering hole 1255d and the upper end 1254a of the eccentric portion 1254. In the former case, i.e., when the distance G1 is greater than the distance G2, the cross-sectional area of ​​the oil scattering hole 1255d is maximized, so that the oil discharged through the oil scattering hole 1255d can scatter further towards the compression portion 130 along the scattering guide 1273. Conversely, in the latter case, where a portion of the oil scattering hole 1255d is blocked by the oil scattering part (more precisely, the fixing part) 1273, resulting in a slight reduction in the cross-sectional area of ​​the oil scattering hole 1255d, the oil discharged through the oil scattering hole 1255d collides with the fixing part 1271, thereby improving the scattering effect. In this embodiment, Figure 6 An example is shown where the gap G1 between the upper end 1254a of the eccentric portion 1254 and the top surface 1273a of the oil scattering guide portion 1273 is greater than the gap G2 between the upper end 1254a of the eccentric portion 1254 and the center Oh of the oil scattering hole 1255d.

[0119] For example, in this embodiment, the scattering guide 1273 can be configured such that its top surface 1273a is at the same height as the lower end P2 of the oil scattering hole 1255d. In other words, the top surface 1273a of the scattering guide 1273 and the lower end P2 of the oil scattering hole 1255d are at the same height. As a result, a portion of the oil scattering from the oil flow path 1255 is guided along the top surface 1273a of the scattering guide 1273 towards the cylinder 1314 side, thereby reaching the vicinity of the highest point P1 of the cylinder 1314.

[0120] Furthermore, at least a portion of the scattering guide 1273 in this embodiment can be located on an imaginary line CL passing through the center of gravity Om of the eccentric mass 1272 and the center Os of the eccentric portion 1254 of the crankshaft 125. For example, the two sides of the circumferential direction of the scattering guide 1273 can be symmetrical about each other with reference to the imaginary line CL. Thus, even if the scattering guide 1273 extends radially from one side of the circumferential direction of the eccentric mass 1272, the center of gravity of the counterweight 127 is still located on the aforementioned imaginary line CL, thereby effectively counteracting the eccentric load generated by the eccentric portion 1254 of the crankshaft 125.

[0121] Furthermore, the scattering guide 1273 of this embodiment can be formed within a predetermined scattering guide range S. For example, such as... Figure 7 As shown, the scattering guide 1273 can be formed within a scattering guide interval S defined as approximately ±45° on both sides of the circumferential direction based on the imaginary line CL. Therefore, by preventing the scattering guide 1273 from being formed too wide in the circumferential direction, even if the scattering guide 1273 is formed on the opposite side of the eccentric mass 1272, the reduction in the eccentric load offsetting effect of the eccentric mass 1272 due to the scattering guide 1273 can be suppressed.

[0122] In this case, the scattering guide 1273 can be formed only in a portion of the aforementioned scattering guide interval S, or it can be formed in the entire scattering guide interval S. In the former case, while forming the scattering guide 1273, it is possible to suppress the halving of the eccentric load offsetting effect of the eccentric mass portion 1272 caused by the scattering guide 1273, and by minimizing the increase in weight of the balance weight 127, it is possible to suppress the decrease in motor efficiency. In the latter case, by maximizing the area of ​​the scattering guide 1273, a large amount of oil scattered from the oil scattering hole 1255d can be guided more smoothly to the space between the cylinder 1314 and the piston 132. This embodiment is described using the former as an example, while the latter is described in another embodiment.

[0123] Furthermore, the scattering guide portion 1273 in this embodiment can be formed with its two sides parallel in the circumferential direction, or it can be formed with a tapered shape in which the gap between the two sides narrows in the direction away from the fixing portion 1271. Thus, while minimizing the area of ​​the scattering guide portion 1273, the radial length of the scattering guide portion 1273 is made as long as possible, thereby enabling a large amount of oil scattered from the oil scattering hole 1255d to be smoothly guided between the cylinder 1314 and the piston 132.

[0124] In this case, the circumferential length L1 of the scattering guide 1273 can be greater than or equal to the radial length L2. In other words, the circumferential length L1 of the scattering guide 1273 can be less than or equal to the length L2 between the inner circumferential surface of the fixing part 1271 and the radial end (hereinafter simply referred to as the end) 1273b of the scattering guide 1273. Thus, a large amount of oil scattered from the oil scattering hole 1255d can be smoothly guided to the space between the cylinder 1314 and the piston 132 while minimizing the radial length L2 of the scattering guide 1273. However, depending on the circumstances, the circumferential length L1 of the scattering guide 1273 can also be less than the radial length L2. In this case, by making the radial length L2 of the scattering guide 1273 as long as possible, the scattering distance can be further increased. This will be explained again later in other embodiments.

[0125] Here, the radial length L2 of the scattering guide 1273 can be formed within a range where the scattering guide 1273 does not collide with the cylinder 1314. For example, as Figure 7 As shown, the spill guide 1273 can be configured such that the distance L3 between the rotation center Oc of the crankshaft 125 and the end 1273b of the spill guide 1273 is less than the shortest distance L4 between the rotation center Oc of the crankshaft 125 and the end 1314a of the cylinder 1314. Therefore, when the counterweight 127 rotates together with the crankshaft 125, the spill guide 1273 of the counterweight 127 will not collide with the cylinder 1314, and can stably guide the oil towards the cylinder 1314 and piston 132.

[0126] Furthermore, in this case, the circumferential length L1 of the oil scattering guide 1273 can be increased or decreased in conjunction with the inner diameter D1 of the oil scattering hole 1255d. For example, as Figure 7 As shown, the circumferential length L1 of the oil splatter guide 1273 can be greater than or equal to the inner diameter D1 of the oil splatter hole 1255d. Therefore, the circumferential length L1 of the oil splatter guide 1273 is appropriately set according to the size of the oil splatter hole 1255d, so that the oil splattered from the oil splatter hole 1255d can be smoothly guided between the cylinder 1314 and the piston 132.

[0127] On the other hand, in this embodiment, the scattering guide 1273 can be formed such that the distance between the two circumferential side surfaces becomes narrower as it moves further away from the fixing part 1271. In other words, the outer circumferential surface of the scattering guide 1273 can be formed into an arc shape that protrudes from the outer circumferential surface of the fixing part 1271. Thus, the circumferential side surface of the scattering guide 1273 is curved, thereby suppressing performance degradation due to flow resistance when the crankshaft 125 rotates. However, depending on the situation, the scattering guide 1273 can also be formed such that the two circumferential side surfaces are parallel to each other. In this case, by increasing the surface area of ​​the scattering guide 1273 relative to the radial length L2, the oil supply effect can be further improved. This will be explained again later in other embodiments.

[0128] On the other hand, the scattering guide portion 1273 of this embodiment can be formed to have the same thickness as the fixing portion 1271. In other words, the thickness t2 of the scattering guide portion 1273 can be formed to have the same thickness as the thickness t1 of the fixing portion 1271. Thus, the scattering guide portion 1273 can extend from the fixing portion 1271 with the same thickness, and the scattering guide portion 1273 can be easily formed.

[0129] However, depending on the circumstances, the thickness t2 of the scattering guide 1273 can also be thinner than the thickness t1 of the fixing part 1271. As a result, the weight of the scattering guide 1273 is reduced, thereby increasing the circumferential length L1 and / or radial length L2 of the scattering guide 1273, thereby increasing the oil supply to the compression part 130.

[0130] On the other hand, the scattering guide 1273 in this embodiment can be formed at the same height as the fixing part 1271. In other words, the top surface 1273a of the scattering guide 1273 can form the same plane as the top surface 1271b of the fixing part 1271. Thus, while facilitating the processing of the scattering guide 1273, it is also possible to guide the oil discharged through the oil scattering hole 1255d to scatter further towards the cylinder barrel 1314.

[0131] However, depending on the circumstances, the top surface 1273a of the scattering guide 1273 can also be inclined or curved, gradually increasing in height axially from the inner circumference to the outer circumference. In this case, even if the circumferential length L1 and / or radial length L2 of the scattering guide 1273 remain unchanged, the scattering guiding effect can be further improved. This will be explained again later in another embodiment.

[0132] On the other hand, although not shown, the scattering guide 1273 can also be formed such that at least a portion overlaps with the imaginary line CL, and the two sides in the circumferential direction are asymmetrical relative to each other based on the imaginary line CL. For example, the scattering guide 1273 can be formed such that a portion overlaps with the imaginary line CL, and is eccentrically positioned to the opposite side relative to the rotation direction of the crankshaft 125. Thus, while minimizing the area of ​​the scattering guide 1273, a large amount of oil scattered from the oil scattering hole 1255d can be smoothly guided to the cylinder 1314 and piston 132 side.

[0133] As described above, when the oil scattering guide 1273 extends radially from the outer peripheral surface of the fixed part 1271, the actual distance from the oil scattering hole 1255d to the compression part 130 can be shortened. Therefore, a large amount of oil scattering from the oil scattering hole 1255d can be more effectively guided to the space between the cylinder 1314 and piston 132 of the compression part 130 via the oil scattering guide 1273. Consequently, oil is smoothly supplied between the cylinder 1314 and piston 132 at both high and low speeds, thereby suppressing refrigerant leakage in the compression chamber 130a to improve cooling capacity and reducing frictional losses between the cylinder 1314 and piston 132 to improve compressor performance. Furthermore, the oil scattering distance can be extended without adding additional components, thus enabling smooth oil supply between the cylinder 1314 and piston 132.

[0134] This can be achieved through Figure 8a and Figure 8b Confirmed. Figure 8a and Figure 8b This is a schematic diagram simulating the scattering distance at different operating speeds with and without the scattering guide 1273.

[0135] Reference Figure 8a Without the scattering guide 1273, when the crankshaft 125 operates at a relatively low speed of 15 rpm, a large amount of oil scattering from the crankshaft 125 reaches a height equivalent to about 2 / 3 of the highest point P1 of the cylinder 1314. When operating at a relatively high speed of 30 rpm, the oil scattering from the crankshaft 125 barely reaches the highest point P1 of the cylinder 1314 or the vicinity of the highest point P1.

[0136] However, refer to Figure 8bWith the scattering guide 1273 provided, when the crankshaft 125 operates at a relatively low speed of 15 rpm, a large amount of oil scattering from the crankshaft 125 reaches a height equivalent to approximately 4 / 5 of the highest point P1 of the cylinder 1314. When operating at a relatively high speed of 30 rpm, the large amount of oil scattering from the crankshaft 125 reaches a height exceeding the highest point P1 of the cylinder 1314. Therefore, with the scattering guide 1273 provided as in this embodiment, a large amount of oil scattering from the crankshaft 125 scatters further towards the compression section 130, thereby more effectively lubricating the cylinder 1314 and piston 132. This allows for smooth lubrication between the cylinder 1314 and piston 132, reducing frictional losses, and effectively seals the gap between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132 to suppress refrigerant leakage in the compression chamber 130a, thereby improving the cooling capacity and / or efficiency of the reciprocating compressor.

[0137] This can be achieved through Figure 9a and Figure 9b Confirmed. Figure 9a and Figure 9b It is a graph comparing the cooling force and energy efficiency at different operating speeds with and without a scattering guide.

[0138] Reference Figure 9a It can be seen that when the balancing counterweight 127 is equipped with a scattering guide 1273 (hereinafter, this embodiment) compared to the case without the scattering guide 1273 (hereinafter, the prior art), the cooling capacity [Q] of the compressor at a relatively low speed is increased by about 1.3%. In other words, when the crankshaft 125 rotates at a speed of 17 rpm, it can be seen that the cooling capacity of the prior art is about 89.35 W, but the cooling capacity of this embodiment is about 90.55 W. Therefore, it can be confirmed that when the crankshaft 125 rotates at a relatively low speed of 17 rpm, the cooling capacity of the compressor in this embodiment is increased by about 1.3% compared to the prior art.

[0139] Conversely, at relatively high speeds, it can be seen that the cooling capacity [Q] of the compressor in this embodiment is increased by approximately 0.5% compared to the prior art. In other words, with the crankshaft 125 rotating at a speed of 30 rpm, it can be seen that the cooling capacity of the prior art is approximately 154.31 W, but the cooling capacity of this embodiment is approximately 155.07 W. Thus, it can be confirmed that when the crankshaft 125 rotates at a relatively high speed of 30 rpm, the cooling capacity of the compressor in this embodiment is increased by approximately 0.5% compared to the prior art.

[0140] Additionally, refer to Figure 9bAt relatively low speeds, it can be seen that the compressor efficiency [EER] of this embodiment is improved by approximately 0.8% compared to the prior art. In other words, with the crankshaft 125 rotating at a speed of 17 rpm, it can be seen that the compressor efficiency of the prior art is approximately 9.22 W, but the compressor efficiency of this embodiment is approximately 9.30 W. Therefore, it can be confirmed that when the crankshaft 125 rotates at a relatively low speed of 17 rpm, the compressor efficiency of this embodiment is improved by approximately 0.8% compared to the prior art.

[0141] Conversely, at relatively high speeds, it can be seen that the compressor efficiency [EER] of this embodiment is improved by approximately 0.6% compared to the prior art. In other words, when the crankshaft 125 rotates at a speed of 30 rpm, it can be seen that the compressor efficiency of the prior art is approximately 8.95 W, but the compressor efficiency of this embodiment is approximately 9.012 W. Thus, it can be confirmed that when the crankshaft 125 rotates at a relatively high speed of 30 rpm, the compressor efficiency of this embodiment is improved by approximately 0.6% compared to the prior art. Thus, it can be confirmed that when a balancing weight 127 is applied to the eccentric portion 1254 of the crankshaft 125 and a scattering guide portion 1273 extending to the opposite side of the eccentric mass portion 1272, i.e., the compression portion 130 side, is formed on the balancing weight 127, the cooling capacity and compressor efficiency of the compressor are improved, and this improvement is particularly significant at low-speed operation.

[0142] On the other hand, other embodiments of the balancing weight will be described below.

[0143] That is, in the aforementioned embodiments, the circumferential length of the scattering guide is greater than or equal to the radial length, but depending on the circumstances, the circumferential length of the scattering guide may also be less than the radial length.

[0144] Figure 10 This is a top view showing a balancing counterweight with a scattering guide provided in another embodiment.

[0145] Reference Figure 10 The basic structure and function of the counterweight 127 in this embodiment are similar to those in the aforementioned embodiments. For example, the counterweight 127 in this embodiment may include a fixing part 1271 inserted into and fixed to the eccentric part 1254 of the crankshaft 125, an eccentric mass part 1272 extending radially from one side of the outer peripheral surface of the fixing part 1271 to form an eccentric load, and a spill guide part 1273 extending radially from the other side of the outer peripheral surface of the fixing part 1271 to guide the oil spilled from the crankshaft 125 to the compression part 130. The basic structure and function of these fixing parts 1271, eccentric mass parts 1272, and spill guide parts 1273 are substantially the same as those in the aforementioned embodiments; therefore, the description of the aforementioned embodiments will be used instead of their description.

[0146] However, in this embodiment, the circumferential length L1 of the scattering guide 1273 may also be less than the radial length L2. In other words, the scattering guide 1273 may be formed so that the radial direction is longer than the circumferential direction. In this case, the end 1273b of the scattering guide 1273 may extend closer to the cylinder 1314 and the piston 132.

[0147] As described above, when the circumferential length L1 of the scattering guide 1273 is less than the radial length L2, the radial length L2 of the scattering guide 1273 can extend further toward the cylinder 1314. Thus, the end 1273b of the scattering guide 1273 can extend closer to the cylinder 1314 side. Therefore, even if the circumferential length L1 of the scattering guide 1273 is shorter than in the aforementioned embodiment, a large amount of oil scattered from the crankshaft 125 can reach near the highest point P1 of the cylinder 1314 under both high-speed and low-speed operation. This shortens the circumferential length (width) L1 of the scattering guide 1273, allows for smoother lubrication between the cylinder 1314 and piston 132 to reduce frictional losses, and suppresses refrigerant leakage from the compression chamber 130a through the gap between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132, thereby improving the cooling capacity and / or efficiency of the reciprocating compressor.

[0148] On the other hand, another embodiment of the balancing weight will be described below.

[0149] That is, in the aforementioned embodiments, the scattering guide portion is formed in a circular or arc shape, but depending on the circumstances, the outer peripheral surface of the scattering guide portion may also be formed in a rectangular shape.

[0150] Figure 11 This is a top view showing a balancing counterweight with a scattering guide provided in another embodiment.

[0151] Reference Figure 11 The basic structure and function of the counterweight 127 in this embodiment are similar to those in the aforementioned embodiments. For example, the counterweight 127 in this embodiment may include a fixing part 1271 inserted into and fixed to the eccentric part 1254 of the crankshaft 125, an eccentric mass part 1272 extending radially from one side of the outer peripheral surface of the fixing part 1271 to form an eccentric load, and a spill guide part 1273 extending radially from the other side of the outer peripheral surface of the fixing part 1271 to guide the oil spilled from the crankshaft 125 to the compression part 130. The basic structure and function of these fixing parts 1271, eccentric mass parts 1272, and spill guide parts 1273 are substantially the same as those in the aforementioned embodiments; therefore, the description of the aforementioned embodiments will be used instead of their description.

[0152] However, in this embodiment, the scattering guide portion 1273 can also be formed as a rectangle that is longer in the radial direction. For example, the scattering guide portion 1273 can be formed such that at least a portion of the interval between the two circumferential side surfaces is the same in the radial direction; in other words, the two circumferential side surfaces can be parallel to each other. Thus, while keeping the circumferential length L1 and / or radial length L2 of the scattering guide portion 1273 constant, the surface area of ​​the top surface 1273a of the scattering guide portion 1273 can be increased.

[0153] In this case, the scattering guide 1273 can be formed such that its radial length L2 is longer than its circumferential length L1, or conversely, its circumferential length L1 is longer than its radial length L2. In the former case, the scattering guide 1273 is closer to the cylinder 1314 side, thereby guiding the scattering of oil; in the latter case, the scattering guide range S of the scattering guide 1273 can be expanded. This embodiment shows an example where the radial length L2 of the scattering guide 1273 is longer than its circumferential length L1.

[0154] Furthermore, in this case, the end portion 1273b of the scattering guide portion 1273, which connects the two circumferential sides of the scattering guide portion 1273, can be formed as a plane or as a curved surface. This embodiment shows an example where the end portion 1273b of the scattering guide portion 1273 is formed as a plane.

[0155] As described above, when the scattering guide 1273 is formed as a rectangle or a rectangle with curved edges, the overall area can be increased while maintaining the same circumferential length as in the previous embodiment. Therefore, even if the radial length L2 of the scattering guide 1273 is the same as or shorter than in the previous embodiment, a large amount of oil scattered from the crankshaft 125 can reach the vicinity of the highest point P1 of the cylinder 1314 under both high-speed and low-speed operation. This shortens the radial length L2 of the scattering guide 1273, allows for smoother lubrication between the cylinder 1314 and piston 132 to reduce frictional losses, and suppresses refrigerant leakage from the compression chamber 130a through the gap between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132, thereby improving the cooling capacity and / or efficiency of the reciprocating compressor.

[0156] Although not shown in the figure, the circumferential length L1 of the scattering guide 1273 can also be formed to increase as it moves further away from the fixing part 1271. In this case, the area of ​​the scattering guide 1273 can be further increased than in the aforementioned embodiment. Thus, even if the radial length L2 of the scattering guide 1273 is further shortened, as the area of ​​the scattering guide (more precisely, the end of the scattering guide) 1273 increases, a large amount of oil scattered through the oil scattering hole 1255d can be more smoothly guided between the cylinder 1314 and the piston 132.

[0157] On the other hand, another embodiment of the balancing weight will be described below.

[0158] That is, in the aforementioned embodiments, the two sides of the circumferential direction of the scattering guide of the balancing counterweight are formed symmetrically around an imaginary line passing through the center of gravity of the eccentric mass and the center of the eccentric part. However, depending on the situation, the scattering guide may also be formed eccentrically relative to the imaginary line.

[0159] Figure 12 This is a top view showing a balancing counterweight with a scattering guide provided in another embodiment.

[0160] Reference Figure 12 The basic structure and function of the counterweight 127 in this embodiment are similar to those in the aforementioned embodiments. For example, the counterweight 127 in this embodiment may include a fixing part 1271 inserted into and fixed to the eccentric part 1254 of the crankshaft 125, an eccentric mass part 1272 extending radially from one side of the outer peripheral surface of the fixing part 1271 to form an eccentric load, and a spill guide part 1273 extending radially from the other side of the outer peripheral surface of the fixing part 1271 to guide the oil spilled from the crankshaft 125 to the compression part 130. The basic structure and function of these fixing parts 1271, eccentric mass parts 1272, and spill guide parts 1273 are substantially the same as those in the aforementioned embodiments; therefore, the description of the aforementioned embodiments will be used instead of their description.

[0161] However, in this embodiment, the scattering guide 1273 can extend radially from the outer peripheral surface of the fixing part 1271 and be eccentrically formed in the circumferential direction. For example, the scattering guide 1273 can be eccentrically formed such that it is spaced apart by a predetermined interval in the circumferential direction from the imaginary line CL passing through the center of gravity Om of the eccentric mass part 1272 and the center Os of the eccentric part 1254. In this case, the scattering guide 1273 can be eccentrically formed in the direction of centrifugal force action, that is, the opposite direction of rotation of the crankshaft 125 to the downstream side of the imaginary line CL. Thus, while minimizing the area of ​​the scattering guide 1273, a large amount of oil scattered from the oil scattering hole 1255d can be smoothly guided to the cylinder 1314 and piston 132 side.

[0162] As described above, when the oil scattering guide 1273 is eccentrically formed relative to the imaginary line CL in the opposite direction of the crankshaft 125's rotation, most of the oil scattering from the oil scattering hole 1255d of the crankshaft 125 is dispersed downstream of the imaginary line CL by the centrifugal force generated when the crankshaft 125 rotates. At this time, since the oil scattering guide 1273 is located downstream of the imaginary line CL, a large amount of oil scattering from the oil scattering hole 1255d can move further along the oil scattering guide 1273 towards the compression section 130. Therefore, even at high and low speeds, a large amount of oil scattering from the crankshaft 125 can reach the vicinity of the highest point P1 of the cylinder 1314, thereby more effectively lubricating the area between the cylinder 1314 and the piston 132. This reduces the area of ​​the scattering guide 1273, smoothly lubricates the cylinder 1314 and piston 132 to reduce friction loss, and suppresses refrigerant leakage in the compression chamber 130a through the gap between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132, thereby improving the cooling capacity and / or efficiency of the reciprocating compressor.

[0163] On the other hand, another embodiment of the balancing weight will be described below.

[0164] That is, in the aforementioned embodiments, the scattering guide portion of the balancing counterweight is formed within a portion of the range of the guide protrusion, but depending on the circumstances, the scattering guide portion may also be formed within the entire range of the guide protrusion.

[0165] Figure 13 and Figure 14 This is a top view showing a balancing counterweight with a scattering guide provided in another embodiment.

[0166] Reference Figure 13 and Figure 14 The basic structure and function of the counterweight 127 in this embodiment are similar to those in the aforementioned embodiments. For example, the counterweight 127 in this embodiment may include a fixing part 1271 inserted into and fixed to the eccentric part 1254 of the crankshaft 125, an eccentric mass part 1272 extending radially from one side of the outer peripheral surface of the fixing part 1271 to form an eccentric load, and a spill guide part 1273 extending radially from the other side of the outer peripheral surface of the fixing part 1271 to guide the oil spilled from the crankshaft 125 to the compression part 130. The basic structure and function of these fixing parts 1271, eccentric mass parts 1272, and spill guide parts 1273 are substantially the same as those in the aforementioned embodiments; therefore, the description of the aforementioned embodiments will be used instead of their description.

[0167] However, in this embodiment, the scattering guide portion 1273 can be formed over the entire scattering guide interval S. For example, the two ends of the scattering guide portion 1273 can be formed at ±45 degrees to both sides in the circumferential direction, based on an imaginary line CL passing through the center of gravity Om of the eccentric mass portion 1272 and the center Os of the eccentric portion 1254 of the crankshaft 125. In this case, the scattering guide portion 1273 can be formed as described above, with both sides in the circumferential direction symmetrical about the aforementioned imaginary line CL, or it can be formed asymmetrically.

[0168] Furthermore, in this situation, the dispersion guide unit 1273 can be used as follows: Figure 13 As shown, the spacing between the two circumferential sides is narrower the further away from the fixing part 1271, or as... Figure 14 As shown, the spacing between the two circumferential sides is the same in the radial direction. In the former case, the weight of the scattering guide 1273 can be reduced, and the scattering guide range S can be expanded as much as possible. In the latter case, the scattering guide range S is expanded to the maximum extent, so that the oil scattering distance achieved by the scattering guide 1273 can be made farther even at low speeds.

[0169] As described above, when the scattering guide 1273 is formed over the entire scattering guide interval S, the circumferential length L1 of the scattering guide 1273 is increased, thereby increasing the effective amount of oil guided from the oil scattering hole 1255d to the cylinder 1314 side through the scattering guide 1273. Therefore, even if the radial length L2 of the scattering guide 1273 is shorter than in the aforementioned embodiment, a large amount of oil scattering from the crankshaft 125 can reach near the highest point P1 of the cylinder 1314. Thus, while forming a smaller radial length L2 of the scattering guide 1273, lubrication between the cylinder 1314 and the piston 132 is smoother, and the gap between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132 can be effectively sealed. This allows for smooth lubrication between the cylinder 1314 and the piston 132, reducing frictional losses and suppressing refrigerant leakage in the compression chamber 130a through the gap between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132, thereby improving the cooling capacity and / or efficiency of the reciprocating compressor.

[0170] On the other hand, another embodiment of the balancing weight will be described below.

[0171] That is, in the aforementioned embodiments, the top surface of the scattering guide of the balancing counterweight is formed flat, but depending on the situation, the top surface of the scattering guide may also be formed inclined or curved.

[0172] Figure 15This is a cross-sectional view showing a balancing counterweight with a scattering guide in another embodiment.

[0173] Reference Figure 15 The basic structure and function of the counterweight 127 in this embodiment are similar to those in the aforementioned embodiments. For example, the counterweight 127 in this embodiment may include a fixing part 1271 inserted into and fixed to the eccentric part 1254 of the crankshaft 125, an eccentric mass part 1272 extending radially from one side of the outer peripheral surface of the fixing part 1271 to form an eccentric load, and a spill guide part 1273 extending radially from the other side of the outer peripheral surface of the fixing part 1271 to guide the oil spilled from the crankshaft 125 to the compression part 130. The basic structure and function of these fixing parts 1271, eccentric mass parts 1272, and spill guide parts 1273 are substantially the same as those in the aforementioned embodiments; therefore, the description of the aforementioned embodiments will be used instead of their description.

[0174] However, in this embodiment, the top surface 1273a of the scattering guide 1273 may not be flat. In other words, the height of the side of the top surface 1273a of the scattering guide 1273 that is farther from the fixing part 1271 may be higher than the side that is closer to the fixing part 1271. For example, the top surface 1273a of the scattering guide 1273 may be inclined or curved, gradually increasing in height as it approaches the end 1273b of the scattering guide 1273 from the fixing part 1271. In this case, the scattering guide 1273 may be formed as described above, with both sides in the circumferential direction symmetrical about the aforementioned imaginary line CL, or it may be formed asymmetrical. In addition, in this case, the scattering guide 1273 may be formed such that the distance between the two circumferential side surfaces, i.e., the circumferential length L1, becomes narrower the farther away from the fixing part 1271, or it may be formed such that the circumferential length L1 is the same in the radial direction. Furthermore, in this case, the scattering guide 1273 can be formed in a portion of the aforementioned scattering guide interval S, or it can be formed in the entire scattering guide interval S. The effects of these various embodiments can be similar to those described above.

[0175] As described above, when the top surface 1273a of the oil scattering guide 1273 is inclined or curved, the oil scattering from the oil scattering hole 1255d moves upward along the top surface 1273a of the oil scattering guide 1273 while scattering radially. Therefore, at both high and low speeds, the oil can scatter further from the oil scattering hole 1255d towards the cylinder 1314 and piston 132. Thus, even if the circumferential length L1 and / or radial length L2 of the oil scattering guide 1273 is shorter than in the aforementioned embodiment, a large amount of oil scattering from the crankshaft 125 can reach near the highest point P1 of the cylinder 1314. Consequently, while forming a smaller area of ​​the oil scattering guide 1273, lubrication between the cylinder 1314 and piston 132 is smoother, and the gap between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132 can be effectively sealed. This allows for smooth lubrication between the cylinder 1314 and the piston 132, reducing frictional losses and suppressing refrigerant leakage in the compression chamber 130a through the gap between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132, thereby improving the cooling capacity and / or efficiency of the reciprocating compressor.

[0176] On the other hand, another embodiment of the balancing weight will be described below.

[0177] That is, in the aforementioned embodiments, the scattering guide of the counterweight is located at the same height as the lower end of the oil flow path outlet, but depending on the circumstances, the scattering guide may also be located at a lower position than the lower end of the oil flow path outlet.

[0178] Figure 16 This is a cross-sectional view showing the assembly position of the balancing weight for this embodiment.

[0179] Reference Figure 16 The basic structure and function of the counterweight 127 in this embodiment are similar to those in the aforementioned embodiments. For example, the counterweight 127 in this embodiment may include a fixing part 1271 inserted into and fixed to the eccentric part 1254 of the crankshaft 125, an eccentric mass part 1272 extending radially from one side of the outer peripheral surface of the fixing part 1271 to form an eccentric load, and a spill guide part 1273 extending radially from the other side of the outer peripheral surface of the fixing part 1271 to guide the oil spilled from the crankshaft 125 to the compression part 130. The basic structure and function of these fixing parts 1271, eccentric mass parts 1272, and spill guide parts 1273 are substantially the same as those in the aforementioned embodiments; therefore, the description of the aforementioned embodiments will be used instead of their description.

[0180] However, in this embodiment, the fixing part 1271 can be attached to a position lower than the outlet of the oil flow path 1255. In other words, the scattering guide part 1273 can be attached to a position lower than the lower end P2 of the oil scattering hole 1255d. This prevents the fixing part 1271 of the balance weight 127 from excessively obstructing the oil scattering hole 1255d due to machining errors and / or assembly errors, thereby improving the assemblability and / or reliability of the balance weight 127.

[0181] In this case, although the top surface 1273a of the oil splatter guide 1273 is lower than the lower end P2 of the oil splatter hole 1255d, the oil splatter guide 1273 can be located adjacent to the oil splatter hole 1255d. For example, the oil splatter guide 1273 can be positioned such that the distance G3 between the top surface 1273a of the oil splatter guide 1273 and the center Oh of the oil splatter hole 1255d is less than or equal to the inner diameter D1 of the oil splatter hole 1255d. This improves the assemblability and / or reliability of the counterweight 127, and ensures that the oil splatter guide 1273 of the counterweight 127 is not too far from the lower end P2 of the oil splatter hole 1255d, thus enabling smooth oil guidance between the cylinder 1314 and the piston 132.

[0182] Furthermore, in this case, the scattering guide portion 1273 can be formed as described above, with both sides in the circumferential direction symmetrical about the aforementioned imaginary line CL, or it can be formed asymmetrically. Additionally, in this case, the scattering guide portion 1273 can be formed such that its circumferential length L1 becomes narrower the further away from the fixing portion 1271, or it can be formed such that its circumferential length L1 is the same in the radial direction. Furthermore, in this case, the top surface 1273a of the scattering guide portion 1273 can be formed flat, or it can be inclined or curved, becoming higher the closer it gets to the end 1273b of the scattering guide portion 1273. Furthermore, in this case, the scattering guide portion 1273 can be formed within a portion of the aforementioned scattering guide interval S, or it can be formed within the entire scattering guide interval S. The effects of these various embodiments are similar to the effects described above.

[0183] As described above, when the scattering guide 1273 is located lower than the lower end P2 of the oil scattering hole 1255d, in other words, when it is fixed at a distance smaller than or equal to the inner diameter D1 of the oil scattering hole 1255d, the scattering guide 1273 will not be too far away from the oil scattering hole 1255d. Therefore, a large amount of oil scattering from the oil scattering hole 1255d can be smoothly supplied along the scattering guide 1273 to the space between the cylinder 1314 and the piston 132. Thus, by preventing the fixing part (or scattering guide) 1271 of the balance weight 127 from blocking the oil scattering hole 1255d due to machining errors and / or assembly errors of the balance weight 127, the oil drawn upward through the oil flow path 1255 can be smoothly supplied to the compression unit 130 and / or the electric unit.

[0184] On the other hand, another embodiment of the balancing weight will be described below.

[0185] That is, in the aforementioned embodiment, the oil slick hole is formed by penetrating the eccentric part of the crankshaft, but depending on the situation, the oil flow path may also penetrate the upper end of the eccentric part.

[0186] Figure 17 This is a cross-sectional view showing the assembly position of the balancing weight for this embodiment.

[0187] Reference Figure 17 The basic structure and function of the counterweight 127 in this embodiment are similar to those in the aforementioned embodiments. For example, the counterweight 127 in this embodiment may include a fixing part 1271 inserted into and fixed to the eccentric part 1254 of the crankshaft 125, an eccentric mass part 1272 extending radially from one side of the outer peripheral surface of the fixing part 1271 to form an eccentric load, and a spill guide part 1273 extending radially from the other side of the outer peripheral surface of the fixing part 1271 to guide the oil spilled from the crankshaft 125 to the compression part 130. The basic structure and function of these fixing parts 1271, eccentric mass parts 1272, and spill guide parts 1273 are substantially the same as those in the aforementioned embodiments; therefore, the description of the aforementioned embodiments will be used instead of their description.

[0188] However, in this embodiment, the end of the oil flow path that forms the outlet can also be formed by penetrating the upper end 1254a of the eccentric portion 1254 of the crankshaft 125. In other words, omitting the oil splatter hole 1255d in the aforementioned embodiment (or even if the oil splatter hole is formed), the outlet end of the oil flow path 1255 can be formed by penetrating the upper end 1254a of the eccentric portion 1254 of the crankshaft 125. In this case, the fixing part 1271 of the balance weight 127 can be inserted and coupled to the outer peripheral surface of the eccentric portion 1254, and can be fixedly coupled near the upper end 1254a of the eccentric portion 1254. In other words, the splatter guide 1273 can be coupled at a position where the distance G1′ between the top surface 1273a of the splatter guide 1273 and the upper end 1254a of the eccentric portion 1254 is less than or equal to the inner diameter D2 of the third oil flow path 1255c at the upper end of the eccentric portion.

[0189] For example, the top surface 1271b of the fixing part 1271, i.e., the top surface 1273a of the scattering guide part 1273, and the upper end 1254a of the eccentric part 1254 can be located on the same line. In this case, the scattering guide part 1273 can be formed as described above, with both sides in the circumferential direction symmetrical about the aforementioned imaginary line CL, or it can be formed asymmetrically. In addition, in this case, the scattering guide part 1273 can be formed such that the circumferential length L1 becomes narrower the further away from the fixing part 1271, or it can be formed such that the circumferential length L1 is the same in the radial direction. In addition, in this case, the top surface 1273a of the scattering guide part 1273 can be formed flat, or it can be inclined or curved, becoming higher the closer to the end 1273b of the scattering guide part 1273. In addition, in this case, the scattering guide part 1273 can be formed in a part of the aforementioned scattering guide interval S, or it can be formed in the entire scattering guide interval S. The effects of these various embodiments can be similar to those described above.

[0190] As described above, when the outlet of the oil flow path 1255 passes through the upper end 1254a of the eccentric portion 1254 of the crankshaft 125, the fixing portion 1271 of the counterweight 127 can be attached near the upper end 1254a of the eccentric portion 1254. For example, the top surface 1273a of the scattering guide portion 1273 and the upper end 1254a of the eccentric portion 1254 are on the same line, in other words, they form the same plane. Thus, a portion of the oil scattering from the oil flow path 1255 is guided along the top surface 1273a of the scattering guide portion 1273 to the cylinder 1314 side, thereby reaching the vicinity of the highest point P1 of the cylinder 1314. As a result, while facilitating the machining of the crankshaft 125 including the oil flow path 1255, the cylinder 1314 and piston 132 are smoothly lubricated, and the gap between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132 can be effectively sealed. This allows for smooth lubrication between the cylinder 1314 and the piston 132, reducing frictional losses and suppressing refrigerant leakage in the compression chamber 130a through the gap between the inner circumferential surface of the cylinder 1314 and the outer circumferential surface of the piston 132, thereby improving the cooling capacity and / or efficiency of the reciprocating compressor.

[0191] Although not shown in the figure, the fixing part 1271 of the counterweight 127 can also be connected to the upper end 1254a of the eccentric part 1254 of the crankshaft 125 at a predetermined interval. In this case, the interval G1 between the upper end 1254a of the eccentric part 1254 and the top surface 1271b of the fixing part 1271 of the counterweight 127 can be less than or equal to the inner diameter D2 of the oil flow path 1255. Its effect is the same as described above. Figure 16 The embodiments are similar.

[0192] On the other hand, in the aforementioned embodiment, the scattering guide 1273 extends from the fixing part 1271, but depending on the situation, only the fixing part 1271 may be formed, and the scattering guide 1273 of the aforementioned embodiment may be omitted. In other words, even if the scattering guide 1273 is omitted from the fixing part 1271, if the fixing part 1271 is located on the same line as the upper end 1254a of the eccentric part 1254 that constitutes the lower end P2 of the oil scattering hole 1255d and / or the outlet height of the oil flow path 1255, or at a position lower than the lower end P2 of the oil scattering hole 1255d and / or the upper end 1254a of the eccentric part 1254 (for example, the distance between the top surface of the fixing part and the center of the oil scattering hole and / or the upper end of the eccentric part is smaller than the inner diameter of the oil scattering hole and / or the inner diameter of the oil flow path), a large amount of oil scattering from the oil flow path 1255 can still scatter further along the top surface 1271b of the fixing part 1271 towards the cylinder 1314. The resulting effect will be explained by referring to the foregoing embodiment instead of its description.

Claims

1. A reciprocating compressor, wherein, include: The outer casing stores a specified amount of oil; The electric motor, located inside the housing, provides driving force; The compression section uses the driving force of the electric unit to cause the piston to reciprocate inside the cylinder to compress the refrigerant. The crankshaft is provided with an eccentric portion that is off-center relative to the rotation center, and is provided with an oil flow path to draw the oil stored in the housing upward toward the eccentric portion; as well as A counterweight is attached to the eccentric part of the crankshaft and rotates together with the crankshaft; The balancing weight includes: A fixing part is attached to the eccentric part of the crankshaft; An eccentric mass portion extends radially eccentrically from the fixed portion; and The scattering guide extends from the fixed part in a direction opposite to the eccentric mass part, and guides the oil scattered from the oil flow path toward the compression part side.

2. The reciprocating compressor according to claim 1, wherein, At least a portion of the scattering guide is located on an imaginary line passing through the center of gravity of the eccentric mass and the center of the eccentric part of the crankshaft.

3. The reciprocating compressor according to claim 2, wherein, The two sides of the circumferential direction of the scattering guide are formed symmetrically with respect to the imaginary line.

4. The reciprocating compressor according to claim 2, wherein, The scattering guide portion is asymmetrically shaped with the imaginary line as a reference, becoming eccentric on the opposite side of the rotation direction of the crankshaft.

5. The reciprocating compressor according to claim 1, wherein, The scattering guide portion is formed eccentrically to one side in the circumferential direction relative to the imaginary line passing through the center of gravity of the eccentric mass portion and the center of the eccentric portion of the crankshaft.

6. The reciprocating compressor according to claim 5, wherein, The scattering guide is formed on the opposite side of the crankshaft's rotation direction.

7. The reciprocating compressor according to claim 1, wherein, The scattering guide is formed such that its circumferential length is greater than or equal to its radial length.

8. The reciprocating compressor according to claim 1, wherein, The scattering guide is formed such that its circumferential length is less than or equal to its radial length.

9. The reciprocating compressor according to claim 1, wherein, The scattering guide portion is formed such that the interval between the two circumferential sides narrows as it moves away from the fixing portion.

10. The reciprocating compressor according to claim 1, wherein, The scattering guide portion is formed such that at least a portion of the interval between the two circumferential side surfaces is the same in the radial direction.

11. The reciprocating compressor according to claim 1, wherein, The distance between the rotation center of the crankshaft and the end of the flyaway guide is less than the shortest distance between the rotation center of the crankshaft and the end of the cylinder.

12. The reciprocating compressor according to claim 1, wherein, An oil splatter hole is formed on the crankshaft, extending from the oil flow path and penetrating the outer peripheral surface of the eccentric portion; The circumferential length of the scattering guide is greater than or equal to the inner diameter of the oil scattering hole.

13. The reciprocating compressor according to claim 1, wherein, An oil splatter hole is formed on the crankshaft, extending from the oil flow path and penetrating the outer peripheral surface of the eccentric portion; The distance between the upper end of the eccentric part and the top surface of the oil scattering guide part is greater than or equal to the distance between the upper end of the eccentric part and the center of the oil scattering hole.

14. The reciprocating compressor according to claim 13, wherein, The top surface of the scattering guide is at the same height as the lower end of the oil scattering hole.

15. The reciprocating compressor according to claim 13, wherein, The top surface of the scattering guide is located lower than the lower end of the oil scattering hole; The distance between the lower end of the oil scattering hole and the top surface of the scattering guide is less than or equal to the inner diameter of the oil scattering hole.

16. The reciprocating compressor according to claim 1, wherein, The oil flow path passes through the upper end of the eccentric part; The distance between the upper end of the eccentric part and the top surface of the scattering guide part is less than or equal to the inner diameter of the oil flow path at the upper end of the eccentric part.

17. The reciprocating compressor according to claim 1, wherein, The scattering guide portion is formed to have the same thickness as the fixing portion.

18. The reciprocating compressor according to claim 1, wherein, The scattering guide portion is thinner than the fixing portion.

19. The reciprocating compressor according to claim 1, wherein, The top surface of the scattering guide and the top surface of the fixing part form the same plane.

20. The reciprocating compressor according to claim 1, wherein, The top surface of the scattering guide is inclined or has a curved topography, which increases axially as it approaches the outer periphery from the inner periphery of the scattering guide.

21. The reciprocating compressor according to any one of claims 1 to 20, wherein, The scattering guide is formed on both sides of the circumference within a range of ±45 degrees, with an imaginary line passing through the center of gravity of the eccentric mass and the center of the eccentric part of the crankshaft as a reference.

22. The reciprocating compressor according to claim 21, wherein, The dispersion guide is formed within a portion of the range.

23. The reciprocating compressor according to claim 21, wherein, The dispersion guide is formed throughout the entire range of the area.

24. A reciprocating compressor, wherein, include: The outer casing stores a specified amount of oil; The electric motor, located inside the housing, provides driving force; The compression section uses the driving force of the electric unit to cause the piston to reciprocate inside the cylinder to compress the refrigerant. The crankshaft has an eccentric portion offset from the center of rotation and an oil flow path for drawing oil stored in the housing upward toward the eccentric portion; and A counterweight is attached to the eccentric part of the crankshaft and rotates together with the crankshaft; An oil splatter hole is formed on the outer peripheral surface of the eccentric part, through which one end of the oil flow path passes. A fixing part is provided on the counterweight to surround and connect to the eccentric part of the crankshaft. The fixing part is attached to a position where the distance between the top surface of the fixing part and the center of the oil splatter hole is less than or equal to the inner diameter of the oil splatter hole.

25. The reciprocating compressor according to claim 24, wherein, The fixing part is combined with the top surface of the fixing part being at the same height as the lower end of the oil splatter hole.

26. The reciprocating compressor according to claim 24, wherein, The top surface of the fixing part forms a single plane along the radial direction.

27. The reciprocating compressor according to claim 24, wherein, The top surface of the fixing part is formed such that its axial height increases as it approaches the outer peripheral surface from the inner peripheral surface of the fixing part.

28. The reciprocating compressor according to any one of claims 24 to 27, wherein, The counterweight also includes a spill guide, which extends radially from the outer peripheral surface of the fixed part and guides the oil spilled from the oil flow path toward the compression part.

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