CN210087602U - Scroll compressor having a discharge port - Google Patents

Scroll compressor having a discharge port Download PDF

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Publication number
CN210087602U
CN210087602U CN201920706869.6U CN201920706869U CN210087602U CN 210087602 U CN210087602 U CN 210087602U CN 201920706869 U CN201920706869 U CN 201920706869U CN 210087602 U CN210087602 U CN 210087602U
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CN
China
Prior art keywords
valve
scroll
gasket
scroll compressor
pressure chamber
Prior art date
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Application number
CN201920706869.6U
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Chinese (zh)
Inventor
李文永
赵灿杰
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LG Electronics Inc
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LG Electronics Inc
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Filing date
Publication date
Priority to KR1020180059217A priority Critical patent/KR20190134054A/en
Priority to KR10-2018-0059217 priority
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/18Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
    • F04C28/22Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/70Use of multiplicity of similar components; Modular construction

Abstract

The utility model discloses a scroll compressor can include: a casing having an inner space divided into a suction space and a discharge space; a first scroll which is disposed in the inner space of the housing and is coupled to the rotating shaft to perform a orbiting motion; a second scroll engaged with the first scroll to form a compression chamber, and formed with at least one bypass hole for bypassing refrigerant of the compression chamber to the outside of the compression chamber to vary a compression capacity; a back pressure chamber assembly disposed on a back surface of the second scroll, and forming a back pressure chamber for pressing the second scroll in a direction of the first scroll; and a gasket valve, the gasket valve comprising: a gasket part disposed between the second scroll and the back pressure chamber assembly to seal between the second scroll and the back pressure chamber assembly; and a valve portion extending from an inner circumferential surface of the pad portion toward the bypass hole, for opening and closing the bypass hole.

Description

Scroll compressor having a discharge port
Technical Field
The utility model relates to a compressor especially relates to scroll compressor.
Background
In the scroll compressor, a non-orbiting scroll is provided in an inner space of a casing, and an orbiting scroll is provided to be engaged with the non-orbiting scroll to perform an orbiting motion. Two compression chambers in pairs, each of which is composed of a suction chamber, an intermediate pressure chamber, and a discharge chamber, are formed between a non-orbiting scroll lap of a non-orbiting scroll and an orbiting scroll lap of a orbiting scroll.
The scroll compressor can obtain a higher compression ratio than other types of compressors and has the characteristic that the suction stroke, the compression stroke and the discharge stroke of refrigerant can be stably connected. As a result, the scroll compressor has an advantage that a stable torque can be obtained, and is therefore widely used for compressing refrigerant in air conditioners and the like.
In the scroll compressor, when the orbiting scroll performs an orbiting motion, a slight gap in the axial direction exists between the non-orbiting scroll and the orbiting scroll. When the compressor is operated, the non-orbiting scroll and the orbiting scroll may be opened in an axial direction due to a gas force of a compressed refrigerant. In order to prevent this, a back pressure system is known in which the orbiting scroll is pressed against the non-orbiting scroll, or conversely, the non-orbiting scroll is pressed against the orbiting scroll.
In these back pressure systems, in a system in which the non-orbiting scroll is pressed toward the orbiting scroll, the non-orbiting scroll is not fixed and is disposed so as to be movable in the axial direction, and a back pressure chamber assembly for pressing the non-orbiting scroll is coupled to the back surface of the non-orbiting scroll.
On the other hand, a scroll compressor is provided with a bypass hole and a bypass valve for opening and closing the bypass hole to prevent excessive compression. The bypass hole may be provided in plural, and thus the bypass valve may be provided in plural. In the prior art (korean laid-open patent No. 10-1462943), a technique of forming a plurality of bypass valves as a whole, thereby reducing the manufacturing and assembling work of the corresponding bypass valves is disclosed.
However, in the conventional scroll compressor as described above, the bypass valve is fastened to the non-orbiting scroll by means of bolts or rivets. Therefore, not only a process of additionally manufacturing the bypass valve is required, but also there is a problem in that the number of parts such as bolts or rivets for fastening the bypass valve and an assembly process are increased.
In addition, in the conventional scroll compressor, since a bolt or a rivet for fastening the bypass valve occupies a space, a vacant space on the rear surface of the non-orbiting scroll becomes narrow. Therefore, the number of bypass valves is limited, thereby having a limitation in improving the performance and reliability of the compressor.
Further, in the conventional scroll compressor, a space for accommodating a bolt or a rivet for fastening the bypass valve is required in the back pressure chamber assembly. However, the space becomes a dead volume (dead volume), so that the performance of the compressor is degraded. Thus, when the retainer is used, the dead volume is further increased, so that the performance of the compressor is further degraded. Moreover, the length of the compressor is also increased.
Further, in the conventional scroll compressor, since the bypass valve is formed of a steel plate, there is also a problem in that a large collision noise is generated when the bypass valve is opened and closed.
Documents of the prior art
Patent document
The prior art is as follows: korean laid-open patent No. 10-1462943 (published: 11 months 12 days 2014)
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide a through forming the bypass valve with adjacent component into a whole to can save the scroll compressor to the manufacturing process and the fastening process of valve.
Another object of the present invention is to provide a scroll compressor in which a valve can be coupled between a non-orbiting scroll and a back pressure chamber assembly without directly fastening the valve.
Further, a scroll compressor capable of reducing a dead volume and shortening a length of the compressor since a valve is not directly fastened is provided.
Further, a scroll compressor capable of increasing the number of valves to improve performance and reliability of the compressor since the valves are not directly fastened is provided.
Another object of the present invention is to provide a scroll compressor capable of limiting an opening amount of a valve even without using an additional retainer.
Further, a scroll compressor capable of reducing a dead volume and shortening a length of the compressor due to omission of a retainer is provided.
Further, a scroll compressor capable of effectively limiting the opening amount of the bypass valve even when the retainer is omitted is provided.
Another object of the present invention is to provide a scroll compressor capable of reducing the collision noise generated when the bypass valve is opened and closed.
In order to achieve the object of the present invention, there may be provided a scroll compressor in which a gasket is provided on a back surface of a non-orbiting scroll, and a valve is formed to extend from an inner circumferential surface of the gasket.
Here, the gasket is closely attached to the non-orbiting scroll, and the valve may be detachably attached to the non-orbiting scroll while rotating around the gasket.
And, an opening restriction groove may be formed in a member opposed to a back surface of the non-orbiting scroll, the opening restriction groove being received when the valve is opened, for restricting an opening amount of the valve.
Also, the gasket and the surface of the valve may be formed of a rubber material.
Furthermore, in order to realize the object of the present invention, there can be provided a scroll compressor comprising: a casing having an inner space divided into a suction space and a discharge space; a first scroll which is disposed in the inner space of the housing and is coupled to the rotating shaft to perform a orbiting motion; a second scroll engaged with the first scroll to form a compression chamber, and formed with at least one bypass hole for bypassing refrigerant of the compression chamber to the outside of the compression chamber to vary a compression capacity; a back pressure chamber assembly disposed on a back surface of the second scroll, and forming a back pressure chamber for pressing the second scroll in a direction of the first scroll; and a gasket valve, the gasket valve comprising: a gasket part which is closely combined between the second scroll and the back pressure chamber assembly to seal the second scroll and the back pressure chamber assembly; and a valve portion extending from an inner circumferential surface of the pad portion toward the bypass hole, for opening and closing the bypass hole.
Here, a plurality of through holes may be formed in the gasket part, and the through holes may be formed to correspond to fastening holes and fastening grooves for fastening the second scroll and the back pressure chamber assembly in an axial direction.
At least one of the valve portions may be formed at a position where the valve portion overlaps with at least a part of the through hole in the longitudinal direction.
Also, in the packing portion, a portion in which the valve portion extends may be formed in a circular arc shape having a predetermined curvature.
Here, the valve portion may include: a connection portion extending from the pad portion; an opening and closing part extending from the connection part for opening and closing the bypass hole; and a reinforcing portion formed so as to extend further on both sides in the circumferential direction of the connecting portion than on both sides in the circumferential direction of the opening/closing portion.
Also, the reinforcing portion may be formed such that the lateral width increases from the end portion of the valve portion closer to the base portion.
Further, the valve portion may be formed with a thickness-reduced surface that becomes thinner as it goes from the base portion toward the end portion.
Here, a surface of the packing valve contacting at least one side of the second scroll and the back pressure chamber assembly may be formed of a material having an impact absorbing ability.
And, the gasket valve may include: a first member having a relatively high rigidity and disposed inside; and a second member having a higher impact absorbing capacity than the first member and provided outside to form a surface.
Also, the gasket valve may be formed of a rubber material.
Here, in the back pressure chamber assembly, an opening restriction groove for restricting an opening amount of the valve portion may be formed on a surface contacting the second scroll.
Also, the opening restriction groove may be formed in a single piece to correspond to the number of the valve portions.
And, the depth of the opening restriction groove may be formed to be deeper as it becomes farther from the pad part.
The utility model discloses an among the scroll compressor, owing to provide one kind to carry out the sealed gasket between non-swirl vortex dish and the backpressure board and be used for the bypass valve of switching by-pass hole to form into a holistic gasket valve, consequently compare the condition of making gasket and bypass valve respectively alone and assembling and can reduce manufacturing cost.
Further, since the packing portion of the packing valve is fastened without directly fastening the valve portion, a bolt or a rivet for fastening the bypass valve can be omitted, so that the assembling work can be reduced.
Further, since a bolt or a rivet for fastening the bypass valve is omitted, a dead volume due to the bolt or the rivet is reduced, so that it is possible to improve performance of the compressor and to shorten the length of the compressor.
Further, in the scroll compressor of the present invention, since the opening restriction groove is formed in the back pressure plate to restrict the opening amount of the valve portion, it is not necessary to additionally provide a retainer. This reduces the number of parts and the number of assembly steps, thereby reducing the manufacturing cost.
Further, since the retainer is omitted, the dead volume and the length of the compressor can be further reduced.
Further, in the scroll compressor of the present invention, since the surface of the gasket valve functioning as the bypass valve is formed of a material having a strong impact absorbing ability such as rubber, it is possible to reduce valve collision noise generated by collision with the non-orbiting scroll or the back pressure plate when the valve portion of the gasket valve opens and closes the bypass hole.
Further, when the inside of the gasket valve is formed of a steel plate having excellent elasticity, the refrigerant of the compression chamber is rapidly bypassed when the valve portion is rapidly opened and closed due to the elasticity, so that the compressor performance can be improved.
Further, when the cushion valve is formed of a rubber material, the sealing ability of the cushion portion and the impact absorbing ability of the valve portion can be improved. Further, by forming the reinforcing portion in the vicinity of the root portion of the valve portion or forming a thickness-reduced portion that becomes thinner toward the end portion of the valve portion, the rigidity of the valve portion is improved, and thus the valve portion can be opened and closed quickly.
Drawings
Fig. 1 is a longitudinal sectional view showing a variable displacement scroll compressor according to the present invention.
Fig. 2 is a sectional perspective view illustrating a portion of a compression part in the scroll compressor of fig. 1.
Fig. 3 is an exploded perspective view showing a part of a compression portion in the scroll compressor of the present embodiment.
Fig. 4 is a plan view showing the gasket valve of fig. 3, and fig. 5 is a sectional view taken along line v-v of fig. 4.
Fig. 6 is a sectional plan view showing another embodiment of the cushion valve corresponding to the present embodiment.
Fig. 7 is a bottom perspective view of the back pressure plate of the present embodiment.
Fig. 8 is a sectional view showing a state in which a packing valve is accommodated in the opening restriction groove of fig. 7.
Fig. 9 is a sectional view showing another embodiment of the opening restriction groove corresponding to fig. 7.
Fig. 10 is a plan view showing another embodiment of a gasket valve according to the present invention.
Fig. 11 is a sectional view taken along line vi-vi of fig. 10.
Fig. 12 is a plan view showing a gasket valve having a plurality of valve portions according to the present invention.
Detailed Description
Hereinafter, a scroll compressor according to the present invention will be described in detail with reference to an embodiment shown in the accompanying drawings.
Fig. 1 is a longitudinal sectional view showing a variable displacement scroll compressor according to the present invention, and fig. 2 is a sectional perspective view showing a part of a compression portion in the scroll compressor of fig. 1.
Referring to these drawings, in the scroll compressor of the present embodiment, a sealed internal space of the casing 110 is partitioned into a suction space 111 as a low pressure portion and a discharge space 112 as a high pressure portion by a high-low pressure partition plate 115, and the high-low pressure partition plate 115 is provided above a non-orbiting scroll (hereinafter, mixed with a second scroll) 150 described later.
Here, the suction space 111 corresponds to a lower space of the high-low pressure partition plate 115, and the discharge space 112 corresponds to an upper space of the high-low pressure partition plate. The suction pipe 113 is fixed to the suction space 111 of the casing 110 to communicate with each other, and the discharge pipe 114 is fixed to the discharge space 112 of the casing 110 to communicate with each other.
A driving motor 120 including a stator 121 and a rotor 122 is provided in the suction space 111 of the casing 110. The stator 121 is fixed to an inner wall surface of the housing 110 by a hot press, and the rotating shaft 125 is inserted into and coupled to a central portion of the rotor 122. The coil 121a is wound around the stator 121, and the coil 121a is electrically connected to an external power source through a terminal (not shown) coupled to the housing 110.
The lower side of the rotation shaft 125 is rotatably supported by a sub-bearing 117 provided at the lower portion of the housing 110. The sub-bearing 117 is supported by a lower frame 118 fixed to an inner surface of the housing 110, thereby stably supporting the rotation shaft 125.
The bottom surface of the casing 110 forms an oil storage space. The oil stored in the oil storage space is transferred to the upper side through the rotation shaft 125 to be supplied to the driving part and the compression chamber.
The upper end portion of the rotating shaft 125 is rotatably supported by the main frame 130. The main frame 130 is fixedly coupled to an inner wall surface of the casing 110, similarly to the lower frame 118, and a main bearing portion 131 protruding downward is formed on a lower side surface of the main frame 130, and the rotation shaft 125 is inserted into the main bearing portion 131. The inner wall surface of the main bearing portion 131 functions as a bearing surface, and supports the rotation shaft 125 to smoothly rotate together with the oil.
A swirling scroll (hereinafter, used in combination with the first scroll) 140 is disposed on the upper surface of the main frame 130. The first scroll 140 includes: a first end plate portion 141 having a substantially disk shape; and a swirl coil (hereinafter, referred to as a first swirl coil) 142 formed spirally on one side surface of the first end plate 141. The first scroll portion 142 forms a compression chamber P together with a second scroll portion 152 of the second scroll 150, which will be described later.
The first end plate portion 141 of the first scroll 140 is rotatively driven in a state of being supported by the upper side surface of the main frame 130, and at this time, a rotation preventing mechanism such as a cross 136 is provided between the first end plate portion 141 and the main frame 130 to prevent the first scroll 140 from rotating.
Also, a boss portion 143 is formed at a lower side surface of the first end plate portion 141 of the first scroll 140, and the rotary shaft 125 is inserted into the boss portion 143 such that the rotational force of the driving motor 120 is transmitted to the first scroll 140. The first scroll 140 is rotatively driven by the rotational force and the cross 136.
The second scroll 150 meshing with the first scroll 140 is disposed above the first scroll 140. Here, the second scroll 150 is provided to be movable in the up-down direction with respect to the first scroll 140, and specifically, a plurality of guide pins (not shown) inserted into the main frame 130, which are formed at the outer circumferential portion of the second scroll 150, are placed and supported on the upper surface of the main frame 130 in a state of being inserted into a plurality of guide holes (not shown).
The second scroll 150 has a disk-like shape on the upper surface of the main body to form a second end plate 151, and a spiral second scroll 152 meshing with the first scroll 142 of the first scroll 140 is formed on the lower portion of the second end plate 151.
A suction port 153 for sucking the refrigerant existing in the suction space 111 is formed in a side surface of the second scroll 150, and a discharge port 154 for discharging the compressed refrigerant is formed in a substantially central portion of the second end plate portion 151.
As described above, the first scroll portion 142 and the second scroll portion 152 constitute a plurality of compression chambers P, and when the compression chambers revolve toward the discharge port 154, the volumes of the compression chambers are reduced, thereby compressing the refrigerant. Therefore, the pressure in the compression chamber adjacent to the suction port 153 becomes minimum, the pressure in the compression chamber communicating with the discharge port 154 becomes maximum, and the pressure in the compression chamber therebetween constitutes an intermediate pressure having a value between the suction pressure of the suction port 153 and the discharge pressure of the discharge port 154. Since the intermediate pressure is applied to a back pressure chamber 160a, which will be described later, and acts to press the second scroll 150 toward the first scroll 140, a scroll-side back pressure hole (not shown) that communicates with one of the regions having the intermediate pressure and discharges the refrigerant is formed in the second end plate portion 151.
A back pressure plate 161 constituting a part of the back pressure chamber assembly 160 is fastened to an upper portion of the second end plate portion 151 of the second scroll 150 by a plurality of bolts 160 b. The bolts 160b penetrate the back pressure plate 161 in the back pressure chamber 160a and are fastened to the second end plate portion 151 of the second scroll 150.
The back pressure plate 161 includes a support plate portion 162 that contacts the second end plate portion 151 of the second scroll 150. The support plate portion 162 is formed in a hollow annular plate shape, and a plate-side back pressure hole 162a communicating with the scroll-side back pressure hole (not shown) is formed to penetrate therethrough in the axial direction.
First and second annular walls 163, 164 surrounding the inner and outer circumferential surfaces of the support plate 162 are formed on the upper surface of the support plate 162. An annular back pressure chamber 160a is formed by the outer peripheral surface of the first annular wall 163, the inner peripheral surface of the second annular wall 164, and the upper side surface of the support plate portion 162.
An intermediate discharge port 163a communicating with the discharge port 154 of the second scroll 150 is formed in the first annular wall 163, and a valve guide groove 163b into which the check valve 155 is slidably inserted is formed inside the intermediate discharge port 163 a. The check valve 155 selectively opens and closes between the discharge port 154 and the intermediate discharge port 163a, and prevents the discharged refrigerant from returning to the compression chamber.
A floating plate 165 constituting an upper surface of the back pressure chamber 160a is provided above the back pressure chamber 160 a. The back pressure chamber of the floating plate 165 moves in the axial direction with respect to the back pressure plate, and can be attached to and detached from the lower surface of the high-low pressure partition plate 115. When the floating plate 165 contacts the high-low pressure partition plate 115, a sealing function is performed so that the discharged refrigerant is discharged into the discharge space 112 without leaking into the suction space 111.
The scroll compressor according to the present embodiment as described above operates as follows.
That is, when power is applied to the stator 121, the rotation shaft 125 rotates together with the rotor 122.
At this time, the first scroll 140 coupled to the upper end of the rotary shaft 125 performs a orbiting motion with respect to the second scroll 150, and thus, two pairs of compression chambers P are formed between the first scroll 142 and the second scroll 152, and when the two pairs of compression chambers P move from the outside to the inside, the volumes of the compression chambers P are reduced, and the refrigerant is sucked, compressed, and discharged.
At this time, a part of the refrigerant moving along the locus of the compression chamber P passes through the scroll-side back pressure port (not shown) and the plate-side back pressure port 162a and moves into the back pressure chamber 160a before reaching the discharge port 154. Thereby, the back pressure chamber 160a formed by the back pressure plate 161 and the floating plate 165 forms an intermediate pressure.
Therefore, the floating plate 165 is pressed upward to be closely attached to the high-low pressure separation plate 115, and at this time, the discharge space 112 and the suction space 111 of the casing are separated, so that the refrigerant discharged to the discharge space 112 can be prevented from leaking to the suction space 111. In contrast, the back pressure plate 161 receives a downward pressure, thereby pressing the second scroll 150 in the first scroll direction. At this time, the second scroll 150 is in close contact with the first scroll 140, and thus the refrigerant compressed in the compression chamber P can be prevented from leaking between the first scroll 140 and the second scroll 150.
As a result, a series of processes are repeated in which the refrigerant sucked into the suction space of the casing is compressed in the compression chamber and discharged into the discharge space, and the refrigerant discharged into the discharge space is again sucked into the suction space after circulating through the refrigeration cycle.
On the other hand, the scroll compressor as described above may include a bypass hole for bypassing a portion of the refrigerant compressed in the compression chamber in advance before moving to the discharge port, and a valve for opening and closing the bypass hole.
The bypass hole may be formed as an over-compression preventing bypass hole for preventing the pressure of the compression chamber from being excessively compressed, or may be formed as a capacity varying bypass hole functioning to vary the operation mode of the compressor.
The bypass orifice may be set at different positions according to its effect. Therefore, the bypass holes are different only in their formation positions, and their structures are substantially the same. However, the bypass valve may have different shapes and operation modes according to its function. However, hereinafter, a bypass hole formed for excessive compression prevention and a bypass valve for opening and closing the bypass hole will be described by way of example.
Referring again to fig. 1 and 2, a plurality of bypass holes 151a for communicating with the discharge space (more precisely, an intermediate discharge port) 112 from the intermediate pressure chamber are formed in the second end plate portion 151 of the second scroll 150, which is a non-orbiting scroll. The bypass hole 151a communicates with the intermediate discharge port 163a via an opening restriction groove 162b provided in a support plate portion 162 of the back pressure plate 161 described later. As will be described later.
The bypass hole 151a is formed to penetrate from a lower side of the second end plate portion 151 constituting an intermediate pressure chamber to a rear surface of the second end plate portion 151 constituting an outside of the compression chamber. The bypass holes 151a are formed at both sides with an interval of 180 ° with respect to the first wrap 142 so that the intermediate-pressure refrigerant having the same pressure can be bypassed in the inner pockets constituting the first compression chamber and the outer pockets constituting the second compression chamber. However, when the length of the wrap portion of the first wrap portion 142 is asymmetric with respect to the length of the wrap portion of the second wrap portion 152 corresponding to 180 ° (i.e., the length of the first wrap portion 142 in the spiral direction is greater than the length of the second wrap portion 152 in the spiral direction), since the inner and outer pockets form the same pressure at the same crank angle, two bypass holes 151a may be formed at the same crank angle, or only one bypass hole 151a may be formed such that both sides are communicated.
A bypass valve is provided at an outlet side end of each bypass hole 151a to selectively open and close the bypass hole 151a to maintain the pressure of the compression chamber at a predetermined pressure. The bypass valve is a check valve formed as a reed valve for opening and closing the bypass hole in accordance with a pressure difference between the pressure of the intermediate pressure chamber and the discharge space.
The bypass valve may be independently coupled to each bypass hole, but in this case, as described above, the number of parts for fastening the valve is increased, so that the manufacturing cost may be increased. Therefore, it is advantageous to manufacture the bypass valve as one bypass valve having a plurality of valve portions to correspond to the number of bypass holes, thereby performing fastening.
Further, when the bypass valve is formed as one body with the adjacent other member so as to be fastened together with the member, the number of parts and the assembling work can be further reduced. For example, the bypass valve may be manufactured as one piece with the adjacent gasket, thereby being fastened together.
Fig. 3 is an exploded perspective view illustrating a portion of a compression part in a scroll compressor according to the present embodiment, fig. 4 is a plan view illustrating a packing valve in fig. 3, and fig. 5 is a sectional view taken along line v-v of fig. 4.
As shown, the bypass valve of the present embodiment may be formed integrally with the gasket, which will be defined as a gasket valve hereinafter.
The gasket valve 170 of the present embodiment may be formed of two materials. For example, the gasket valve 170 may include an inner first member 170a and an outer surface-forming second member 170 b.
That is, the first member 170a may be formed of a thin steel plate having a relatively high rigidity, or a steel core such as a wire, and the second member 170b may be formed of a rubber material having a higher elasticity than the first member 170 a. Thus, the valve portion 175 can be opened and closed more quickly by the elastic force of the first member 170a, and the impact force can be reduced by the second member 170b, thereby reducing valve collision noise.
Further, the gasket valve of the present embodiment is configured in a shape integrating the gasket function and the valve function as one body as described above. For example, referring to fig. 4, the gasket valve 170 of the present embodiment may include: a gasket part 171 for sealing between the second scroll 150 and the back pressure plate 161 constituting the back pressure chamber assembly 160; and a valve portion 175 extending laterally from an inner circumferential surface of the packing portion 171 toward the bypass hole 151a for opening and closing the bypass hole 151 a.
The pad portion 171 is formed in a ring shape, and a plurality of through holes 171a are formed at appropriate positions in the circumferential direction. The through holes 171a are formed to correspond to the fastening holes 151c and the fastening grooves 162c in the axial direction, the fastening holes 151c and the fastening grooves 162c for fastening the second scroll 150 and the back pressure plate 161. At least one of the valve portions 175 may be formed at a position at least partially overlapping the through hole 171a in the radial direction (more precisely, the longitudinal direction of the valve portion). Thus, although a part of the spacer portion 171 floats up together to form a gap during opening and closing of the valve portion 175, the peripheral portion of the valve portion 175 is fixed more firmly than the other portion by the rivet or bolt 160b passing through the through hole 171a, and the gap can be suppressed from being formed in the spacer portion 171.
Further, a sealing protrusion 171b may be formed on both side surfaces in the axial direction of the packing portion 171. The sealing protrusion 171b is formed in the circumferential direction of the packing part 171, and may be formed to be connected in a manner of surrounding the through hole 171 a. This makes it possible to seal the space between the second scroll 150 and the back pressure plate 161 firmly.
On the other hand, the valve portion 175 may include: a connecting portion 175a constituting an outer end portion and extending from an inner peripheral surface of the pad portion 171; and an opening and closing part 175b constituting an inner end and extending from the connection part 175a to open and close the bypass hole.
Since the side surfaces of both sides in the circumferential direction of the valve portion 175 are formed along a straight line, the connecting portion 175a may be formed in a shape that forms a right angle or an acute angle with the inner circumferential surface of the packing portion 171. However, in this case, the valve portion 175 may be broken due to frequent opening and closing operations. Therefore, in terms of reliability, it is preferable that the portion of the packing portion 171 where the valve portion 175 extends, that is, the root portion of the connecting portion 175a, be formed with a circular arc-shaped curved surface portion 175c having a predetermined curvature.
On the other hand, in the foregoing embodiment, the case where the first member made of a steel plate has the same shape as the entire shape of the cushion valve, that is, the first member and the second member have the same shape, is exemplified. However, the first member and the second member may be formed in different shapes according to different situations. Fig. 6 is a sectional plan view showing another embodiment of the cushion valve corresponding to the present embodiment.
As shown in the drawing, in the gasket valve 170 of the present embodiment, the portion of the first member 170a corresponding to the gasket portion 171 may be formed as narrow as possible, and conversely, the portion corresponding to the valve portion 172 may be formed as wide as possible.
Thus, in the packing part 171, the width of the second member 170b made of a material having a relatively strong impact absorption capability can be formed widely to improve the sealing capability in the packing part 171, and conversely, in the valve part 175, the width of the first member 170a having a relatively high rigidity or elastic force can be formed widely to improve the reaction speed of the valve.
On the other hand, as described above, since the valve portion is formed in the shape of a reed valve having one end extending from the spacer portion, a retainer for limiting the opening amount of the valve portion may be required. However, when the retainer is provided between the second scroll and the back pressure plate, the number of parts increases, so that the assembly work increases. Therefore, as described in the present embodiment, an opening restriction groove functioning as a retainer may be formed at one axial side surface of the back pressure plate constituting the back pressure chamber assembly without providing an additional retainer.
Fig. 7 is a bottom perspective view illustrating the back pressure plate of the present embodiment, fig. 8 is a sectional view illustrating a state in which a packing valve is received in the opening restriction groove of fig. 7, and fig. 9 is a sectional view illustrating another embodiment of the opening restriction groove corresponding to fig. 7.
As shown in fig. 7 and 8, the opening restricting groove 162b of the present embodiment may be formed such that one end of the opening restricting groove 162b communicates with one end of the intermediate discharge port 163 a. Thus, the refrigerant bypassed by the bypass hole 151a can be directly discharged to the intermediate discharge port 163a by opening the restricting groove 162b, thereby minimizing flow resistance.
Further, the opening restriction groove 162b may also be formed widely on one side surface of the back pressure plate 161 so that the plurality of valve portions 175 can be accommodated together. However, in this case, since a portion not corresponding to the valve portion 175 is also formed concavely, a dead volume may increase. Therefore, the opening restriction groove 162b is preferably formed in a single piece to correspond to the number of the valve portions 175.
Further, the opening restriction groove 162b is formed in a shape that can be inserted when the valve portion 175 is opened, and may be formed to the same depth as shown in fig. 8. However, as shown in fig. 9, since the valve portion 175 is opened when the opening/closing portion 175b is rotated about the connecting portion 175a, the opening restriction groove 162b may be formed with an inclined surface 162b1, the inclined surface 162b1 being deeper as it is farther from the pad portion 171 from a position close to the pad portion 171. Thus, the pressure back surface of the valve portion 175 contacts the inclined surface 162b1 of the opening restriction groove 162b from the time point when the valve portion 175 starts to open, and the valve collision noise can be further reduced.
On the other hand, although in the foregoing embodiment, the cushion valve is constituted by the first member having rigidity and the second member having impact absorbing ability, according to circumstances, it may be formed only by the member having predetermined elasticity. Fig. 10 is a plan view showing another embodiment of a gasket valve according to the present invention, and fig. 11 is a sectional view taken along line vi-vi of fig. 10.
As shown in fig. 10 and 11, the pad valve 170 of the present embodiment may be formed in one body using a material having an impact absorbing ability, such as rubber. Thereby, the cushion valve 170 is closely adhered between the second scroll 150 and the back pressure plate 161 in the cushion portion 171, so that the sealing capability is doubled, and at the same time, since the cushion portion and the valve portion are formed as one body, the cushion valve can be easily manufactured.
However, when the pad valve 170 is formed of only a rubber material, the closing operation of the opening and closing part 175 may be delayed due to low restoration capability. In view of this, in the gasket valve 170 of the present embodiment, as shown in fig. 10, reinforcing portions 175d may be further formed on the side surfaces on both sides in the circumferential direction of the valve portion 175.
In this case, the reinforcing portion 175d may be formed in one kind of bulging shape only on the side surfaces on both sides in the circumferential direction of the connecting portion 175a, or may be formed in a tapered shape from the outer peripheral side to the inner peripheral side of the valve portion 175. That is, the reinforcing portion 175d may be formed such that the lateral width of the connecting portion 175a constituting the base portion of the valve portion 175 is larger than the lateral width of the opening and closing portion 175b constituting the tip end of the valve portion 175. Thereby, the rigidity of the connection portion 175a can be improved, and even in the case where the pad valve 170 is formed of only a material having a low recovery ability such as rubber, the opening and closing portion 175b can be closed quickly.
Further, the valve portion 175 may be formed differently in thickness. For example, as shown in fig. 11, the valve portion 175 may be formed thick near the base portion thereof, and may be formed thinner closer to the distal end portion of the valve portion 175. For this reason, in the valve portion 175, an inclined thickness-reduced surface 175e may be formed in the side surface on both sides in the opening and closing direction corresponding to the pressure back surface of the opening restriction groove 162 b. Thus, in the valve portion 175, a predetermined thickness difference t is generated as it comes closer to the end portion from the vicinity of the root portion connected to the spacer portion 171, and when the valve portion 175 is opened, the resistance relatively increases, and conversely, when the valve portion 175 is closed, it is possible to close quickly in response to the resistance.
Thus, as shown in fig. 10, when the valve portion is formed together with the example in which the reinforcing portion 175d is formed in the vicinity of the root portion, the elastic force of the valve portion 175 is doubled, so that it is possible to close quickly.
In the packing valve of the present embodiment as described above, the packing for sealing between the second scroll and the back pressure plate and the bypass valve for opening and closing the bypass hole are formed as a single body as described above, so that the manufacturing cost can be reduced as compared with the case where the packing and the valve are separately manufactured and assembled.
Further, since the surface of the gasket valve of the present embodiment is formed of a material having a strong impact absorbing ability such as rubber, it is possible to reduce valve collision noise generated when opening and closing the bypass hole.
On the other hand, the case with yet another embodiment corresponding to the gasket valve of the present invention is as follows. That is, in the foregoing embodiment, an example in which one pad portion is provided with two valve portions is illustrated and described. However, the valve portion may be formed in three or more as necessary. Fig. 12 is a plan view showing a gasket valve having a plurality of valve portions according to the present invention.
For example, three bypass holes may be formed in each compression pocket, and the three bypass holes may be formed in each compression pocket at regular intervals along the path of each compression chamber.
At this time, as shown in the foregoing embodiment, a plurality of valve portions 175 corresponding to each bypass hole may be formed to protrude from the inner circumferential surface of the packing portion 171 toward each bypass hole.
In this case, a plurality of opening restriction grooves (refer to fig. 10)162b may be formed in the back pressure plate 161 so that each valve portion 175 is accommodated singly or in plurality.
As described above, since the valve portion functioning as the bypass valve is restricted in the opening/closing amount by the opening restriction groove provided in the back pressure plate and functioning as the retainer, the retainer and the bolt for fastening the retainer can be omitted.
Thus, the space utilization rate between the second scroll and the back pressure plate can be improved as compared with the case where the plurality of holders are fastened together with the valve by bolts. Thereby, the number of bypass holes can be sufficiently increased, and the performance and reliability of the compressor can be further improved.
On the other hand, although not shown in the drawings, when the length of the valve portions is different, the radial width and thickness of the valve portions may be made different to appropriately adjust the rigidity corresponding to each valve portion.
On the other hand, in the foregoing embodiment, the case where the bypass hole plays a role of preventing the excessive compression is exemplified, but the foregoing packing valve may be equally applied when the bypass hole plays a role of changing the compression capacity.
On the other hand, in the foregoing embodiment, the low-pressure scroll compressor has been described as an example, but the present invention is equally applicable to a hermetic compressor in which the internal space of the casing is partitioned into the suction space as the low-pressure portion and the discharge space as the high-pressure portion.

Claims (11)

1. A scroll compressor, comprising:
a casing having an inner space divided into a suction space and a discharge space;
a first scroll which is disposed in the inner space of the housing and is coupled to the rotating shaft to perform a orbiting motion;
a second scroll engaged with the first scroll to form a compression chamber, and formed with one or more bypass holes bypassing refrigerant of the compression chamber to the outside of the compression chamber to change compression capacity;
a back pressure chamber assembly disposed on a back surface of the second scroll, forming a back pressure chamber to press the second scroll toward the first scroll; and
a gasket valve, comprising: a gasket portion closely coupled between the second scroll and the back pressure chamber assembly to seal between the second scroll and the back pressure chamber assembly; and a valve portion extending from an inner peripheral surface of the pad portion toward the bypass hole and opening and closing the bypass hole.
2. The scroll compressor of claim 1,
a plurality of through holes are formed in the gasket part, the through holes being formed to correspond to fastening holes and fastening grooves for fastening the second scroll and the back pressure chamber assembly in an axial direction.
3. The scroll compressor of claim 2,
at least one of the valve portions has the through hole formed at a portion thereof connected to the spacer portion in the longitudinal direction of the valve portion.
4. The scroll compressor of claim 3,
a portion of the cushion portion where the valve portion extends is formed in an arc shape having a predetermined curvature.
5. The scroll compressor of claim 1,
the valve portion includes:
a connection portion extending from the pad portion;
an opening/closing portion extending from the connection portion and opening/closing the bypass hole; and
and a reinforcing part formed such that the lateral width of the connecting part is greater than the lateral width of the opening/closing part.
6. The scroll compressor of claim 5,
the reinforcing portion is formed such that the lateral width increases from the end portion of the valve portion toward the root portion.
7. The scroll compressor of claim 5,
the valve portion is formed with a reduced thickness that decreases from the base portion of the valve portion toward the end portion.
8. The scroll compressor of claim 1,
a surface of the gasket valve that contacts at least one of the second scroll and the back pressure chamber assembly is formed of a material having an impact absorbing ability.
9. The scroll compressor of claim 8,
the gasket valve includes:
a first member having a relatively high rigidity and disposed inside the cushion valve; and
a second member having a high impact absorbing capability with respect to the first member and disposed outside the cushion valve to form a surface.
10. The scroll compressor of claim 1,
the gasket valve is formed of a rubber material.
11. The scroll compressor of any one of claims 1 to 10,
an opening restriction groove for restricting an opening amount of the valve portion is formed in a surface of the back pressure chamber assembly facing the second scroll.
CN201920706869.6U 2018-05-24 2019-05-16 Scroll compressor having a discharge port Active CN210087602U (en)

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KR1020180059217A KR20190134054A (en) 2018-05-24 2018-05-24 Scroll compressor
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KR101462943B1 (en) 2013-03-18 2014-11-19 엘지전자 주식회사 Scroll compressor with bypassing means

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