KR20160055496A - Reciprocating compressor and a method for manufacturing the same - Google Patents

Reciprocating compressor and a method for manufacturing the same Download PDF

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Publication number
KR20160055496A
KR20160055496A KR1020140155386A KR20140155386A KR20160055496A KR 20160055496 A KR20160055496 A KR 20160055496A KR 1020140155386 A KR1020140155386 A KR 1020140155386A KR 20140155386 A KR20140155386 A KR 20140155386A KR 20160055496 A KR20160055496 A KR 20160055496A
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KR
South Korea
Prior art keywords
shell
thickness
coupled
hole
assembly
Prior art date
Application number
KR1020140155386A
Other languages
Korean (ko)
Inventor
손인호
조재호
임상현
Original Assignee
엘지전자 주식회사
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Application filed by 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Priority to KR1020140155386A priority Critical patent/KR20160055496A/en
Publication of KR20160055496A publication Critical patent/KR20160055496A/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/14—Provisions for readily assembling or disassembling
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
    • H01R9/00—Structural associations of a plurality of mutually-insulated electrical connecting elements, e.g. terminal strips or terminal blocks; Terminals or binding posts mounted upon a base or in a case; Bases therefor
    • H01R9/16—Fastening of connecting parts to base or case; Insulating connecting parts from base or case
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K33/00—Motors with reciprocating, oscillating or vibrating magnet, armature or coil system
    • H02K33/16—Motors with reciprocating, oscillating or vibrating magnet, armature or coil system with polarised armatures moving in alternate directions by reversal or energisation of a single coil system
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/22—Auxiliary parts of casings not covered by groups H02K5/06-H02K5/20, e.g. shaped to form connection boxes or terminal boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2230/00—Manufacture
    • F05B2230/20—Manufacture essentially without removing material
    • F05B2230/23—Manufacture essentially without removing material by permanently joining parts together
    • F05B2230/232—Manufacture essentially without removing material by permanently joining parts together by welding
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

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

Abstract

The present embodiment relates to a reciprocating compressor, and a method for manufacturing the same. According to the present embodiment, the reciprocating compressor comprises: a shell where a driving unit is installed, having a penetration hole; and a terminal assembly coupled to the penetration hole. The terminal assembly comprises: a first main body having an insertion hole; a terminal pin inserted into the insertion hole and supplying power to the driving unit; an insulation member supporting the terminal pin to be insulated inside the insertion hole; and a second main body extended from the first main body to the inside of the shell and coupled to the shell. A thickness or a width (t1) of the first main body is formed to be larger than the thickness or the width (t2) of the second main body.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a reciprocating compressor,

The present invention relates to a reciprocating compressor and a method of manufacturing the same.

A reciprocating compressor refers to a device for compressing a fluid by sucking and compressing a refrigerant through a reciprocating movement of the piston in a cylinder and discharging the refrigerant. The reciprocating compressor can be classified into a reciprocating compressor and a reciprocating reciprocating compressor according to the driving method of the piston. Here, the connection type reciprocating compressor compresses the refrigerant by reciprocating movement of the piston in the cylinder connected to the rotary shaft of the drive unit via the connecting rod. The reciprocating compressor of the reciprocating type is connected to the mover of the reciprocating motor, And the refrigerant is compressed by the reciprocating motion in the cylinder.

The reciprocating compressor may include an electronic component for applying external power to the compressor, and a terminal assembly for installing the electric wire in the shell.

The present applicant has filed a conventionally-related application with respect to the above-mentioned terminal assembly (hereinafter referred to as the bibliographic information of the conventional application)

1. Public number: 10-2007-0019231 (public date: February 15, 2007)

2. Title of the invention: Terminal assembly of a hermetic compressor

The conventional reciprocating compressor has a problem that the terminal assembly is damaged by the stress or force generated when the terminal assembly is fixed to the shell.

Particularly, in recent years, there is a tendency to reduce the volume of the machine room in which the compressor is installed, in order to expand the storage space of the electric appliance in which the compressor is installed, for example, the refrigerator. To this end, it is necessary to reduce the size of the compressor, in which case the size of the terminal assembly may also be reduced and its stiffness may be weakened. As a result, there is a problem that breakage of the terminal assembly occurs more easily.

In order to solve the above problems, it is an object of the present invention to provide a reciprocating compressor having a rigid terminal assembly.

The reciprocating compressor according to the present embodiment includes a shell provided with a drive unit and having a through hole; And a terminal assembly coupled to the through hole, wherein the terminal assembly includes: a first body having an insertion hole; A terminal pin inserted into the insertion hole and supplying power to the driving unit; An insulating member insulatively supporting the terminal pin inside the insertion hole; And a second body extending from the first body toward the interior of the shell and coupled to the shell, the thickness or width t1 of the first body being greater than the thickness or width t2 of the second body ) Is formed.

The thickness or the width t1 of the first main body is larger than twice or four times the thickness or the width t2 of the second main body.

The thickness or the width t1 of the first main body is a thickness or a width in a direction in which the terminal pin extends through the through hole.

The thickness or the width t2 of the second main body is a thickness or a width in a direction perpendicular to the engagement surface of the shell and the second main body.

The second body may include a through-hole extending from the first body and coupled to the inside of the through-hole; And an engaging portion extending from the penetrating portion toward an inner side of the shell to be coupled to the shell.

The width or the thickness t2 of the penetrating portion is formed to be equal to the width or the thickness t2 of the engaging portion.

The joining portion includes a welded portion welded to the shell.

In addition, the terminal pin may include an insulating portion formed at a central portion of the terminal pin, to which the insulating member is coupled; And non-insulating portions formed on both side portions of the terminal pin, wherein the insulating member is not coupled.

In addition, the insulating member includes glass.

The terminal assembly further includes a terminal bracket coupled to an outer surface of the shell and projecting outwardly from the outside of the terminal assembly.

A method of manufacturing a reciprocating compressor according to another aspect includes the steps of: fabricating an assembly body having at least one insertion hole; Inserting a terminal pin into the insertion hole; Assembling the base material of the insulating member outside the terminal pin; Heating the base material of the insulating member so that the insulating member supports the terminal pin to the assembly body; And coupling the assembly body to the through hole of the shell, wherein the assembly body includes a first body formed with the insertion hole and a second body extended from the first body and coupled to the shell, The thickness t1 of the first body in the first direction is greater than the thickness t2 of the second body in the second direction.

The first direction is a direction in which the first body passes through the through hole, and the second direction is a direction perpendicular to a coupling surface between the shell body and the second body.

The second body includes a penetrating portion extending from the first body and coupled to the inside of the through hole and an engaging portion extending from the penetrating portion toward the inside of the shell to be coupled to the shell, Is a direction perpendicular to an inner circumferential surface of a through hole to which the penetrating portion is coupled or perpendicular to a coupling surface to which the shell and the engaging portion are coupled.

The thickness t1 of the first main body in the first direction is not less than two times and not more than four times the thickness t2 of the second main body in the second direction.

According to the present invention, since the thickness of the first body to which the terminal pin is inserted is greater than the thickness of the second body to be coupled to the shell, the rigidity of the terminal assembly can be secured to a certain level or more .

Particularly, even if the stress generated in the process of bonding or welding the terminal assembly to the shell is transferred to the assembly body, the thickness of the first body may be sufficiently large, so that the stress is applied to the insulation member, It is possible to prevent a phenomenon of breakage.

As a result, breakage of the insulating member or the terminal assembly is prevented, so that leakage of refrigerant or leakage of electricity through the joint portion of the terminal assembly can be prevented.

1 is a perspective view of a reciprocating compressor according to an embodiment of the present invention.
2 is an exploded perspective view of a reciprocating compressor according to an embodiment of the present invention.
3 is a cross-sectional view of a reciprocating compressor according to an embodiment of the present invention.
4 is a view showing a terminal assembly assembled to a shell according to an embodiment of the present invention.
5 is an exploded perspective view showing the construction of a lower shell and a terminal assembly according to an embodiment of the present invention.
6 is a view showing a terminal assembly according to an embodiment of the present invention coupled to a lower shell;
FIGS. 7 and 8 are perspective views showing a configuration of a terminal assembly according to an embodiment of the present invention.
9 is a cross-sectional view showing a terminal assembly according to an embodiment of the present invention coupled to a lower shell;
FIGS. 10A to 10C are views showing an assembly process of the reciprocating compressor according to the embodiment of the present invention.
11 is a graph showing the effect of a terminal assembly according to an embodiment of the present invention.

The present invention will become more apparent by describing in detail preferred embodiments of the present invention with reference to the accompanying drawings. It is to be understood that the embodiments described herein are illustrated by way of example for purposes of clarity of understanding and that the present invention may be embodied with various modifications and alterations. Also, for ease of understanding of the invention, the appended drawings are not drawn to scale, but the dimensions of some of the components may be exaggerated.

FIG. 1 is a perspective view of a reciprocating compressor according to an embodiment of the present invention, FIG. 2 is an exploded perspective view of a reciprocating compressor according to an embodiment of the present invention, FIG. 3 is a sectional view of a reciprocating compressor according to an embodiment of the present invention And FIG. 4 is a view showing a terminal assembly according to an embodiment of the present invention assembled into a shell.

1 to 4, a reciprocating compressor 10 according to an embodiment of the present invention includes a shell 100 forming an outer shell, a driving unit 100 provided in an inner space of the shell 100, A compression unit 300 for receiving a driving force from the driving unit 200 and compressing the refrigerant through a linear reciprocating motion, and a compressor 300 for sucking refrigerant for refrigerant compression of the compression unit 300, And a suction and discharge unit (400) for discharging the compressed refrigerant.

The shell 100 defines a closed space therein, and accommodates various components constituting the compressor 10 in the compressor space. The shell 100 is made of a metal material and includes a lower shell 110 and an upper shell 160.

The lower shell 110 has an approximately hemispherical shape and accommodates various components constituting the preceding drive unit 200, the compression unit 300, the discharge unit 400 and the compressor 10 together with the upper shell 160 Thereby forming a receiving space. The lower shell 110 may be referred to as a " compressor body "and the upper shell 160 may be referred to as a" compressor cover. &Quot;

The lower shell 110 is provided with a suction pipe 120, a discharge pipe 130, a process pipe 140, and a control device 800 for controlling power supply to the compressor 10.

The suction pipe 120 introduces the refrigerant into the shell 100 and is mounted through the lower shell 110. The suction pipe 120 may be separately mounted on the lower shell 110 or integrally formed with the lower shell 110.

The discharge pipe 130 discharges compressed refrigerant in the shell 100 and is mounted through the lower shell 110. The discharge pipe 130 may be separately mounted on the lower shell 110 or integrally formed with the lower shell 110.

The discharge pipe 130 is connected to a discharge hose 790 of a suction and discharge unit 400 to be described later. The refrigerant that has entered the suction pipe 120 and is compressed through the compression unit 300 may be discharged to the discharge pipe 130 through the discharge hose 790 of the suction and discharge unit 400.

The process pipe 140 is provided to fill refrigerant into the shell 100 after closing the inside of the shell 100. The process pipe 140 is connected to the suction pipe 120 and the discharge pipe 130, And can be mounted through the lower shell 110.

The control unit 800 includes a casing 810 and a terminal assembly 170 provided inside the casing 810 for transmitting external power to the drive unit 200 and a terminal assembly 170 And a terminal bracket 870 for protection. The terminal bracket 870 is coupled to the outer surface of the lower shell 110 and is configured to protrude outward from the terminal assembly 170. The terminal bracket 870 may function to protect the terminal assembly 170. For example, the terminal bracket 870 may be welded to the lower shell 110.

A leg 115 is provided at a lower portion of the lower shell 110. The legs 115 allow the compressor 10 to be stably supported at a predetermined installation site or installation surface.

The upper shell 160 forms a receiving space together with the lower shell 110 and is formed in an approximately hemispherical shape like the lower shell 110. The upper shell 160 packages the lower shell 110 on the upper side of the lower shell 110 to form a closed space therein.

The drive unit 200 includes stator units 210 and 220, an insulator 230, a rotor 240, and a rotating shaft 250.

The stator 210 and 220 include a stator core 210 and a stator coil 220 as a fixed portion during driving of the drive unit 200.

The stator core 210 is made of a metal material and may have a substantially cylindrical shape having an inner hollow. The stator coil 220 is mounted inside the stator core 210. The stator coil 220 generates an electromagnetic force when power is supplied from the outside through the terminal assembly 170 to perform electromagnetic interaction with the stator core 210 and the rotor 240. Thus, the driving unit 200 can generate a driving force for reciprocating motion of the compression unit 300.

The insulator 230 is disposed between the stator core 210 and the stator coil 220 and prevents direct contact between the stator core 210 and the stator coil 220. When the stator coil 220 is in direct contact with the stator core 210, the generation of electromagnetic force from the stator coil 220 may be hindered. The insulator 230 may separate the stator core 210 and the stator coil 220 by a predetermined distance.

The rotor 240 is rotatable during operation of the drive unit 200 and is rotatably disposed inside the stator coil 220 and may be installed in the insulator 230. The rotor 240 is provided with a magnet. When the power is supplied from the outside, the rotor 240 rotates through an electromagnetic interaction with the stator core 210 and the stator coil 220. The rotational force generated by the rotation of the rotor 240 acts as a driving force for driving the compression unit 200.

The rotation shaft 250 is installed in the rotor 240 and is installed to penetrate the rotor 240 along the up and down direction and can be rotated together with the rotor 240. The rotating shaft 250 is connected to a connecting rod 340 to transmit a rotational force generated by the rotor 240 to the compression unit 300.

Specifically, the rotating shaft 250 includes a base shaft 252, a rotating plate 254, and an eccentric shaft 256.

The base shaft 252 is mounted in the vertical direction (Z-axis direction) or the vertical direction in the rotor 240. When the rotor 240 rotates, the base shaft 252 may be rotated together with the rotor 240.

The rotation plate 254 is installed on one side of the base shaft 252 and can be rotatably mounted on a rotation plate seating portion 320 of a cylinder block 310 described later.

The eccentric shaft 256 protrudes upward from the upper surface of the rotary plate 254. Specifically, the eccentric shaft 256 protrudes from a position eccentric from the axis center of the base shaft 252, and is eccentrically rotated when the rotary plate 254 rotates. A connecting rod 340 to be described later is mounted on the eccentric shaft 256. With the eccentric rotation of the eccentric shaft 256, the connecting rod 340 linearly reciprocates in the front-rear direction (X-axis direction).

The compression unit 300 includes a cylinder block 310, a connecting rod 340, a piston 350, and a piston pin 370.

The cylinder block 310 is mounted on the driving assembly 200, more specifically, on the upper side of the rotor 240 and inside the shell 100. The cylinder block 310 includes a rotating plate seating portion 320 and a cylinder 330.

The rotating plate seating portion 320 is formed at a lower portion of the cylinder block 310 and rotatably accommodates the rotating plate 254. The rotating plate seating portion 320 is formed with a shaft opening 322 through which the rotating shaft 250 can pass.

The cylinder 330 is provided in the front portion of the cylinder block 310 and is arranged to receive the piston 350 described later. The piston 350 is reciprocatable in the front-rear direction (X-axis direction), and a compression space C capable of compressing the refrigerant is formed in the cylinder 330.

The cylinder 330 may be made of aluminum. For example, the cylinder 330 may be made of aluminum or an aluminum alloy. The magnetic flux generated in the rotor 240 is not transmitted to the cylinder 330 due to the aluminum material which is a nonmagnetic material. Accordingly, the magnetic flux generated in the rotor 240 can be prevented from being transmitted to the cylinder 330 and leaking to the outside of the cylinder 330.

The connecting rod 340 is a device for transmitting the driving force provided from the driving unit 200 to the piston 350 and converts the rotational motion of the rotational shaft 250 into a linear reciprocating motion. Specifically, the connecting rod 340 linearly reciprocates in the forward and backward directions (X-axis direction) when the rotating shaft 250 rotates. The connecting rod 340 may be made of a sintered alloy material.

The piston 350 is a device for compressing the refrigerant and is accommodated in the cylinder 330 such that it can reciprocate in the front-rear direction (X-axis direction). The piston 350 is connected to the connecting rod 340. The piston 350 reciprocates linearly in the cylinder 330 according to the movement of the connecting rod 340. In accordance with the reciprocating movement of the piston 350, the refrigerant introduced from the suction pipe 120 can be compressed in the cylinder 330.

The piston 350 may be made of an aluminum material, such as aluminum or an aluminum alloy, such as the cylinder 330. Therefore, it is possible to prevent the magnetic flux generated in the rotor 240 from leaking to the outside through the piston 350.

In addition, the piston 350 may be made of the same material as the cylinder 330 and have substantially the same thermal expansion coefficient as that of the cylinder 330. The piston 350 is moved in an approximately equal amount to the cylinder 330 in the internal environment of the shell 100 at a high temperature (typically about 100 占 폚) when the compressor 10 is driven, . Therefore, interference between the piston 350 and the cylinder 330 can be prevented from occurring when the piston 350 reciprocates in the cylinder 330.

The piston pin (370) engages the piston (350) and the connecting rod (340). Specifically, the piston pin 370 passes through the piston 350 and the connecting rod 340 in the vertical direction (Z-axis direction) to connect the piston 350 and the connecting rod 340.

The suction and discharge unit 400 includes a muffler assembly 410, a valve assembly 480, a discharge hose 790, a plurality of gaskets 485 and 488, an elastic member 490, and a clamp 492.

The muffler assembly 410 transfers the refrigerant sucked from the suction pipe 120 to the inside of the cylinder 330 and the compressed refrigerant in the compression space C of the cylinder 330 to the discharge pipe 130 . The muffler assembly 410 is provided with a suction space S for receiving the refrigerant sucked from the suction pipe 120 and a discharge space D for accommodating the refrigerant compressed in the compression space C of the cylinder 330, .

In detail, the refrigerant sucked from the suction pipe 120 flows into the suction space S of the suction and discharge tank 426 through suction mufflers 430 and 420 to be described later. The refrigerant compressed in the cylinder 330 passes through the discharge muffler 425 and 438 through the discharge space D of the absorption and discharge tank 426 and flows to the outside of the compressor 10 through the discharge hose 790 And is discharged.

The valve assembly 480 guides the refrigerant in the suction space S into the cylinder 330 or guides the compressed refrigerant in the cylinder 330 to the discharge space D. A discharge valve 483 is provided on the front surface of the valve assembly 480 so as to be openable and closable to discharge the refrigerant compressed in the compression space C to the discharge space D, And a suction valve 481 is provided on the rear surface of the suction chamber S so as to be openable and closable in order to discharge the refrigerant in the suction space S to the compression space C of the cylinder 330. That is, a discharge valve 483 is provided on the front surface of the valve assembly 480, and a suction valve 481 is provided on the rear surface of the valve assembly 420.

The operation of the discharge valve 483 and the suction valve 481 will be briefly described.

The discharge valve 483 is opened and the suction valve 481 is closed. In the compression chamber C in the cylinder 330, Accordingly, the refrigerant compressed in the cylinder 330 can be introduced into the discharge space D without flowing into the suction space S. On the contrary, when the refrigerant introduced into the suction space S into the cylinder 330 is sucked, the discharge valve 483 is closed and the suction valve 481 is opened. Accordingly, the refrigerant in the suction space S can be introduced into the cylinder 330 without being introduced into the discharge space D. [

The discharge hose 790 is a device for transferring the compressed refrigerant contained in the discharge space D to the discharge pipe 130 and is coupled to the muffler assembly 410. One side of the discharge hose 790 is coupled to the muffler assembly 410 so as to communicate with the discharge space D and the other side of the discharge hose 790 is coupled to the discharge pipe 130.

The plurality of gaskets 485 and 488 are installed to one side and the other side of the valve assembly 420 to prevent refrigerant leakage. In detail, the plurality of gaskets 485 and 488 include a first gasket 485 and a second gasket 488. The first gasket 485 is mounted to the front of the valve assembly 480 and the second gasket 488 is mounted to the rear of the valve assembly 420.

The elastic member 490 is for supporting the muffler assembly 410 when the compressor 10 is driven and is mounted in front of the muffler assembly 410. The elastic member 490 includes a plate spring (Belleville Spring).

The clamp 492 secures the valve assembly 480, the first gasket 485, the second gasket 488 and the resilient member 490 to the muffler assembly 410. The clamp 492 has a substantially triple-head shape and can be mounted to the muffler assembly 410 through a fastening means such as a screw member.

The compressor (10) further includes a plurality of damper members (500, 550, 600, 650) and a balance weight (700).

The plurality of damper members 500, 550, 600, and 650 cushion vibration of internal structures generated when the compressor 10 is driven. The plurality of damper members 500, 550, 600 and 650 include a front damper 500, a rear damper 550 and lower dampers 600 and 650.

The front damper 500 cushions the vibration of the suction and discharge unit 400 and may be made of a rubber material. The front damper 500 may be coupled to the front upper portion of the cylinder block 310 through fastening means coupled to the clamp 492.

The rear damper 550 buffers the vibration of the compression unit 300 and is mounted on the rear upper portion of the cylinder block 310. The rear damper 550 may be made of rubber.

The lower dampers (600, 650) buffer the vibration of the drive unit (200) and are provided in plural. The plurality of lower dampers 600 and 650 include a front lower damper 600 and a rear lower damper 650. The front-side lower damper 600 cushions the front-side vibration of the drive unit 200 and is mounted on the front lower side of the stator core 210. The rear lower damper 650 cushions backward vibration of the drive unit 200 and is mounted on the rear lower side of the stator core 210.

The balance weight 700 is an apparatus for controlling the rotational vibration of the drive unit 200 when the rotary shaft 250 rotates and is coupled to the eccentric shaft 256 of the rotary shaft 250 on the upper side of the connecting rod 340 .

FIG. 5 is an exploded perspective view showing a configuration of a lower shell and a terminal assembly according to an embodiment of the present invention, FIG. 6 is a view showing a terminal assembly according to an embodiment of the present invention coupled to a lower shell, 8 is a perspective view showing a configuration of a terminal assembly according to an embodiment of the present invention.

5 through 8, a terminal assembly 170 according to an embodiment of the present invention may be coupled to the lower shell 110.

In detail, the lower shell 110 includes a shell body 111 having a substantially hemispherical shape, which forms a lower outer surface of the compressor 10, and an external power source coupled to the shell body 111, And a terminal assembly 170 for delivering the terminal assembly 170 to the user.

The shell body 111 is formed with a through-hole 113 to which the terminal assembly 170 is coupled. The terminal assembly 170 may be fixed to the shell body 111 through the through-hole 113. At least a portion of the terminal assembly 170 may be located outside the lower shell 110 and the remaining portion may be positioned within the lower shell 110 through the through hole 113.

The terminal assembly 170 includes an assembly body 171 coupled to the through hole 113 and a plurality of terminal pins 172 coupled to the assembly body 171 to perform power supply, And an insulating member 173 for holding the pin 172 in an insulated state.

The assembly main body 171 is provided with a first main body 171a having an insertion hole 175 (see FIG. 10A) through which the plurality of terminal pins 172 are inserted so as to pass through the through hole 113, And a second body 171b extending from the first body 171a to the inner side of the lower shell 110 and coupled to the shell body 111. [

Fig. 7 shows a virtual line l1 indicating the boundary between the first main body 171a and the second main body 171b.

In detail, the first main body 171a has a substantially cylindrical shape and may be called a "cylindrical portion ". The outer circumferential surface of the first body 171a is arranged to pass through the through-hole 113. The insertion hole 175 is formed to penetrate from one surface of the first body 171a toward the other surface. Here, the direction from one surface to the other surface is understood as a direction from the outside of the shell body 111 to the inside.

The second body 171b extends from the first body 171a toward the inner side of the lower shell 110. [ Specifically, the second main body 171b is provided with a penetrating portion 171c penetrating the through hole 113 and an engaging portion 171d extending from the penetrating portion 171c inward of the lower shell 110 ).

For example, the penetrating portion 171c extends from the first main body 171a in an inward direction perpendicular to the shell body 111. [ The engaging portion 171d extends obliquely from the penetrating portion 171c. For example, the engaging portion 171d may extend obliquely in a direction in which its outer diameter gradually increases.

The plurality of terminal pins 172 extend through the insertion hole 175 of the first main body 171a and extend to the inside and the outside of the shell main body 111. At least a portion of the plurality of terminal pins 172 may be located inside the shell body 111 and the remaining portion may be located outside the shell body 111 through the insertion hole 175. [ have.

The plurality of terminal pins 172 include an insulating portion 172a and non-breaking portions 172b and 172c. The insulating portion 172a forms a substantially central portion of the terminal pin 172 and is understood as a portion where the insulating member 173 is covered.

The non-knotted portions 172b and 172c form both side portions of the terminal pin 172 and are understood as portions where the insulating member 173 is not covered. The non-breakable portions 172b and 172c include a first non-breakable portion 172b positioned outside the shell body 111 and a second non-breakable portion 172c positioned inside the shell body 111 .

The insulating member 173 supports the plurality of terminal pins 172 so that the plurality of terminal pins 172 can be insulated from the assembly body 171. The insulating member 173 is disposed so as to surround the outer side of the insulating portion 172a. For example, the insulating member 173 may be made of a glass material, and may be coupled to the outer portion of the insulating portion 172a through a melting process after being assembled to the insulating portion 172a. The insulating member 173 may be positioned to penetrate the insertion hole 175.

9 is a cross-sectional view showing a terminal assembly according to an embodiment of the present invention coupled to a lower shell;

9, a terminal assembly 170 according to an embodiment of the present invention includes a first body 171a on which an insertion hole 175 is formed and a second body 171b on which the shell body 111 And a second body 171b extending inward.

The second main body 171b is provided with a penetrating portion 171c positioned inside the through hole 113 and an inclined portion 171c extending obliquely from the penetrating portion 171c inward of the shell main body 111, 111). The engaging portion 171d includes a welded portion 171e welded to the shell body 111. [

The thickness or the width t1 of the first body 171a in the first direction may be greater than the thickness or the width t2 of the second body 171b in the second direction.

The first direction may correspond to a direction in which the first main body 171a passes through the through hole 113 or a direction in which the terminal pin 172 extends through the through hole 113. [ In other words, the first direction can be understood as a direction from the inside of the shell main body 111 to the outside of the shell main body 111 with respect to the through hole 113.

The second direction may correspond to a direction perpendicular to the coupling surface of the shell body 111 and the second body 171b. That is, the thickness of the penetrating portion 171c in the second direction is understood as a thickness in a direction perpendicular to the inner circumferential surface of the through hole 113 to which the penetrating portion 171c is coupled. The thickness of the engaging portion 171d in the second direction is understood as a thickness in a direction perpendicular to the engaging surface to which the shell body 111 and the engaging portion 171d are engaged. The welding portion 171e is formed on the coupling surface to which the coupling portion 171d is coupled.

The thickness t2 of the penetrating portion 171c in the second direction and the thickness t2 of the engaging portion 171d in the second direction may be the same.

The thickness or the width t1 of the first main body 171a in the first direction is larger than twice or twice the thickness t2 in the second direction of the second main body 171b, . In one example, t1 may be 4.5 mm, and t2 may be 1.5 mm.

The size of the terminal assembly 170 according to the embodiment of the present invention may be smaller than that of a conventional terminal assembly for miniaturization of the compressor. Accordingly, the force or stress generated when the terminal assembly 170 is engaged with the lower shell 110 can relatively act as a large load on the terminal assembly 170. Here, the "size" may be understood as the height of the first main body 171a (refer to FIG. 9).

However, since t1 is formed to be sufficiently larger than t2, the force or stress generated in the process of coupling the terminal assembly 170 to the shell main body 111 is transmitted to the first main body 171a The size of the insulating member 173 can be reduced by appropriately dispersing or absorbing the entire area of the first main body 171a. That is, since the force or the stress can be dispersed over the entire area of the insulating member 173, the insulating member 173 or the terminal pin 172 can be prevented from being damaged by the force or the stress have.

As a result, even if the compressor and the terminal assembly 170 are miniaturized, the thickness of the portion of the assembly main body 171 where the terminal pin 172 and the insulating member 173 are combined is increased, It can be stably coupled to the main body 111, and refrigerant or electric leakage in the compressor can be prevented.

When the thickness or the width t1 of the first main body 171a in the first direction is smaller than twice the thickness or the width t2 of the second main body 171b in the second direction, Or the effect of dispersing or absorbing the stress may be small.

On the other hand, when the thickness or the width t1 of the first main body 171a in the first direction is larger than four times the thickness or the width t2 of the second main body 171b in the second direction As the size of the terminal assembly 170 is increased, the thickness of the lower shell 110 must be increased. As a result, the size of the compressor is increased and the material cost is increased.

A welding agent may be provided between the terminal assembly 170 and the shell body 111 in the process of joining the terminal assembly 170 to the shell body 111, The terminal assembly 170 and the shell body 111 can be coupled to each other while the welding agent melts.

FIGS. 10A to 10C are views showing an assembly process of the reciprocating compressor according to the embodiment of the present invention.

10A to 10C, a step of manufacturing an assembly body 171 having a first body 171a having an insertion hole 175 and a second body 171b coupled to the shell body 111 . Here, the thickness of the first main body 171a may be sufficiently larger than the thickness of the second main body 171b as described above.

Next, a step of inserting a plurality of terminal pins 172 into the insertion hole 175 is performed. Then, a step of assembling the base material of the insulating member 173 to the outside of the terminal pin 172 is performed. At this time, the base material of the insulating member 173 may be coupled to the outside of the insulating portion 172a of the terminal pin 172. [

A step of heating the base member of the insulating member 173 in a state where it is assembled to the terminal pin 172 is performed. The heating temperature can be determined as the temperature at which the base material of the insulating member 173 can be melted. The insulating member 173 is formed in the process of cooling the base material of the insulating member 173 after being melted. The insulating member 173 stably supports the terminal pin 172 on the assembly main body 171.

Through this process, the manufacture of the terminal assembly 170 is completed. Then, a step in which the terminal assembly 170 is coupled to the lower shell 110 is performed (see FIG. 5).

Specifically, the terminal assembly 170 or the shell body 111 is provided with a welding agent, and the terminal assembly 170 is inserted into the through-hole 113 of the shell body 111. In this process, the terminal assembly 170 or the shell body 111 can be heated, and the terminal assembly 170 and the shell body 111 are engaged while the welding agent melts.

When the coupling is completed, the first body 171a protrudes to the outside of the shell body 111 and the second body 171b can be supported by the shell body 171b. The thickness of the first body 171a is formed to be greater than the thickness of the second body 171b so that the insulating member 173 is formed by the force or the stress transmitted from the second body 171b, Or the terminal pin 172 may be prevented from being damaged.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is clearly understood that the same is by way of illustration and example only and is not to be construed as limiting the scope of the invention as defined by the appended claims. It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the present invention.

11 is a graph showing the effect of a terminal assembly according to an embodiment of the present invention.

Referring to Fig. 11, the pressing force acting on the terminal assembly and the change in refrigerant leakage rate are shown, depending on the thickness of the assembly body. The unit of the pressing force is kgf, and the refrigerant leakage rate represents a leak rate after the terminal assembly is coupled in a state where a predetermined amount of refrigerant is filled in the shell.

Case 1 shows a conventional terminal assembly structure in which the size of the first main body, that is, the vertical height (reference in FIG. 9) is relatively large, and the thicknesses of the first main body and the second main body in the assembly main body are equal to t1. Here, t1 may be 1.4 mm, for example.

In this case, the pressing force acting on the terminal assembly in the process of joining to the lower shell of the terminal assembly is 20 kgf, and the refrigerant leakage rate is 38%. Since the size of the first main body is large, the area of welding (welding) between the terminal assembly and the shell is increased, so that the pressing force is relatively small. However, since the pressing force is concentrated on the insulating member through the first body having a small thickness, the refrigerant leakage rate is relatively large.

Case 2 shows a conventional terminal assembly structure in which the size of the first main body, that is, the vertical height (reference in FIG. 9) is relatively large, and the thicknesses of the first main body and the second main body in the assembly main body are equal to t2. Here, t2 may be 1.5 mm, for example.

In this case, the pressing force acting on the terminal assembly during the engagement with the lower shell of the terminal assembly is 28 kgf, and the refrigerant leakage rate represents 35%.

Case 3 and Case 4 show the case where the thickness of the first body is larger than the thickness of the second body according to the present invention. For example, Case 3 shows the case where the thickness of the first body is 4.5 mm and the thickness of the second body is 1.4 mm. Case 4 shows the case where the thickness of the first body is 4.5 mm and the thickness of the second body is 1.5 mm.

In Case 3, the pressing force acting on the terminal assembly in the process of joining to the lower shell of the terminal assembly is 32 kgf, and the refrigerant leakage rate is 5%. In Case 4, the pressing force acting on the terminal assembly during the engagement of the terminal assembly with the lower shell is 28 kgf, and the refrigerant leakage rate is 0.4%.

Under experimental conditions, if the refrigerant leakage rate is greater than the reference leakage rate (Lp), it can be judged that the reliability of the compressor is not suitable for the required level. That is, it can be understood that this reliability level is not satisfied in the case of the terminal assemblies according to cases 1 and 2, while it can be understood that this reliability level is satisfied in the case of the terminal assemblies according to cases 2 and 3. [ For example, the reference leak rate Lp may be 10%.

In summary, in the case of the terminal assembly according to the present embodiment, since the size of the terminal assembly is small, the area (welded area) of the terminal assembly and the shell is small and accordingly the pressing force can be relatively large. However, since the pressing force is dispersed in the insulating member through the first body having a large thickness, breakage of the insulating member is prevented, and thus the leakage rate of the refrigerant can be relatively small.

Accordingly, when the first body to which the insulating member is coupled is formed to have a relatively large thickness as in the present embodiment, breakage of the insulating member is prevented, and the refrigerant leakage rate can be significantly reduced.

10: compressor 100: shell
110: lower shell 111: shell body
113: Through hole 170: Terminal assembly
171: Assembly body 171a:
171b: second body 172: terminal pin
173: Insulation member 800: Control device
810: Casing 870: Terminal bracket

Claims (14)

A shell provided with a drive unit and having a through hole;
A terminal assembly coupled to the through-hole,
In the terminal assembly,
A first body having an insertion hole;
A terminal pin inserted into the insertion hole and supplying power to the driving unit;
An insulating member insulatively supporting the terminal pin inside the insertion hole; And
A second body extending from the first body in an inward direction of the shell and coupled to the shell,
Wherein the thickness or the width t1 of the first body is larger than the thickness or the width t2 of the second body. The method according to claim 1,
Wherein the thickness or the width t1 of the first body is greater than twice and less than four times the thickness or width t2 of the second body. The method according to claim 1,
Wherein the thickness or the width t1 of the first main body is a thickness or a width in a direction in which the terminal pin extends through the through hole. The method of claim 3,
Wherein the thickness or the width (t2) of the second main body is a thickness or a width in a direction perpendicular to the engagement surface of the shell and the second main body. 5. The method of claim 4,
In the second main body,
A through-hole extending from the first body and coupled to the inside of the through-hole; And
And a coupling portion extending from the penetrating portion toward an inner side of the shell and coupled to the shell. 6. The method of claim 5,
The width or thickness (t2)
Is formed to be the same as the width or the thickness (t2) of the engaging portion. 6. The method of claim 5,
Wherein the coupling portion includes a welded portion welded to the shell. The method according to claim 1,
The terminal pin
An insulating portion formed at a central portion of the terminal pin and coupled to the insulating member; And
And a non-insulating portion formed on both side portions of the terminal pin and not connected to the insulating member. The method according to claim 1,
Wherein the insulating member includes glass. The method according to claim 1,
Further comprising a terminal bracket coupled to the outer surface of the shell and projecting outwardly from the outside of the terminal assembly. Manufacturing an assembly body having at least one insertion hole;
Inserting a terminal pin into the insertion hole;
Assembling the base material of the insulating member outside the terminal pin;
Heating the base material of the insulating member so that the insulating member supports the terminal pin to the assembly body; And
Coupling the assembly body to the through-hole of the shell,
The assembly body includes a first body formed with the insertion hole and a second body extending from the first body and coupled to the shell,
Wherein the thickness t1 of the first body in the first direction is greater than the thickness t2 of the second body in the second direction. 12. The method of claim 11,
Wherein the first direction is a direction in which the first body passes through the through hole,
Wherein the second direction is a direction perpendicular to a mating surface of the shell body and the second body. 13. The method of claim 12,
The second body includes a penetrating portion extending from the first body and coupled to the inside of the through hole and an engaging portion extending from the penetrating portion toward the inside of the shell to be coupled to the shell,
Wherein the second direction is a direction perpendicular to an inner circumferential surface of the through hole to which the penetrating portion is coupled or a direction perpendicular to a coupling surface to which the shell and the engaging portion are coupled. 13. The method of claim 12,
Wherein the thickness t1 in the first direction of the first main body is formed to be at least two times and not more than four times the thickness t2 in the second direction of the second main body. .
KR1020140155386A 2014-11-10 2014-11-10 Reciprocating compressor and a method for manufacturing the same KR20160055496A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108591025A (en) * 2018-06-25 2018-09-28 海门亿峰机械零部件制造有限公司 A kind of compressor of air conditioner upper shell cover and terminal base structure

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108591025A (en) * 2018-06-25 2018-09-28 海门亿峰机械零部件制造有限公司 A kind of compressor of air conditioner upper shell cover and terminal base structure

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