CN216922509U - Compressor - Google Patents

Abstract

The present invention relates to a compressor including a compression mechanism adapted to compress a fluid and a silencing partition for partitioning an inner space of the compressor into a high pressure side and a low pressure side, the silencing partition including a mounting hole and an insert installed in the mounting hole, a fluid compressed by the compression mechanism being discharged to the high pressure side via a passage of the insert and then to an outside of the compressor, the insert being in interference fit with the mounting hole to have an interference fit portion, and a convex section protruding toward the high pressure side with respect to a remaining portion of the silencing partition being provided at a portion of the silencing partition adjacent to the interference fit portion. The present invention provides a compressor improved in a sound deadening configuration and safety reliability.

Description

Compressor

Technical Field

The present invention relates to a compressor, and more particularly, to a compressor improved in noise reduction structure and safety and reliability.

Background

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

In the field of compressors, for example, scroll compressors belong to positive displacement compression machines. The compression mechanism of a scroll compressor generally includes a non-orbiting scroll member and an orbiting scroll member. The vanes of the non-orbiting and orbiting scroll members engage each other to compress a working fluid (e.g., refrigerant). Generally, after a working fluid is introduced into a compression mechanism from a suction port, compression of the working fluid is achieved by movement of a fixed scroll part and a movable scroll part, and a compressed high-pressure gas is discharged through a discharge port.

The compressor further includes a partition plate for partitioning an inner space of the compressor into a high pressure side and a low pressure side, and an insert is generally provided in a through hole of the partition plate, and a fluid compressed by the compression mechanism is discharged to the high pressure side (discharge space) and then to the outside of the compressor through a passage of the insert. In this sound deadening configuration, the insert is fitted with interference fit with the through hole of the partition plate to generate a retaining force for overcoming the closing force (i.e., the gas force based on the pressure difference between the high pressure side and the low pressure side to which the insert is subjected). The pressure difference between the high pressure side and the low pressure side tends to apply a force downward to the insert, so that the through-hole portion of the partition plate, which is interference-fitted with the insert, is enlarged, resulting in a reduction in the retention force to the insert with an increase in the pressure difference, a reduction in the retention safety coefficient (retention/closing force) of the partition plate, and a reduction in the operational reliability of the compressor. The muffler partition retention safety factor of the prior art compressor muffler construction is low and typically 1.8 lower than the production safety muffler partition retention safety factor.

Furthermore, the muffling configuration of the related art compressor is intended to increase the retention force by increasing the interference fit between the insert and the partition, however this is limited by the yield strength of the partition, while also increasing the risk of compressor failure.

Therefore, there is a need for further improvement in sound emission configuration and safety reliability of the prior art compressor.

SUMMERY OF THE UTILITY MODEL

The present invention provides a compressor having an improved noise reduction structure and safety and reliability by providing a boss section at an adjacent portion of an interference fit portion where an insert of a noise reduction partition plate is interference-fitted with a mounting hole.

The present invention provides a compressor including a compression mechanism adapted to compress a fluid and a silencing partition for partitioning an inner space of the compressor into a high pressure side and a low pressure side, the silencing partition including a mounting hole and an insert installed in the mounting hole, a fluid compressed by the compression mechanism being discharged to the high pressure side via a passage of the insert to be discharged to an outside of the compressor, the insert being in interference fit with the mounting hole to have an interference fit portion, and a convex portion section protruding toward the high pressure side with respect to a remaining portion of the silencing partition being provided at a portion of the silencing partition adjacent to the interference fit portion.

Advantageously, the mounting hole is provided at the raised section.

Advantageously, the sound-deadening partition has a substantially frustoconical cylindrical shape, the mounting hole is provided at the center of the sound-deadening partition, and the sound-deadening partition further includes a main inclined section.

Advantageously, the angle of taper of the primary slope section a is greater than 10 ° and less than 60 °.

Advantageously, the sound-attenuating partition further comprises a transition arc between the main inclined section and the convex section, the convex section protruding in the direction of the high pressure side relative to the transition arc so as to have a protrusion height H starting from a tangent to the transition arc.

Advantageously, the convex section is connected to the main inclined section, the convex section comprising a convex inclined portion inclined at a greater taper angle connected to the main inclined section and a convex horizontal portion extending substantially horizontally from the convex inclined portion, thereby having a protrusion height H starting from the point of connection of the convex section to the main inclined section.

Advantageously, the projection height H is greater than 1mm and/or less than 5 times the thickness T of the sound-attenuating partition.

Advantageously, the raised section is configured as a plurality of connected segments in a multi-step shape.

Advantageously, the mounting hole is a circular hole having a diameter D greater than 50 mm.

Advantageously, the insert is cylindrical and has a bottom wall with a through hole to allow fluid to be discharged to the high pressure side via the insert, and a check valve for selectively opening and closing the through hole is provided at the insert.

Advantageously, the sound-attenuating barrier and the insert are configured and mated such that the insert has a retention safety factor with respect to the sound-attenuating barrier greater than 2.0.

Advantageously, the compressor is an inverter scroll compressor.

Thus, the present invention provides a compressor improved in a sound deadening configuration and safety and reliability as compared with the prior art.

Drawings

Features and advantages of embodiments of the present invention will become more readily appreciated from the following description with reference to the accompanying drawings, in which:

FIG. 1 illustrates a longitudinal cross-sectional view of a related art scroll compressor showing an interference fit insert and a sound-attenuating barrier.

Fig. 2 shows a longitudinal cross-sectional view of a sound-attenuating partition and its associated components of a scroll compressor in accordance with a first embodiment of the present invention, wherein the sound-attenuating partition is provided with a raised section in the vicinity of the interference fit of the sound-attenuating partition with the insert, and the sound-attenuating partition further has a main sloped section and a transitional arc.

FIG. 3 illustrates a longitudinal cross-sectional view of a sound-attenuating partition and its associated components of a scroll compressor in accordance with a second embodiment of the present invention, wherein the sound-attenuating partition is provided with a raised section in the vicinity of the interference fit of the sound-attenuating partition with the insert, and the sound-attenuating partition also has a main sloped section but no transition arc.

Fig. 4 shows a longitudinal sectional view of a sound-deadening partition plate of a scroll compressor and its related components according to a modification of the first embodiment of the present invention, in which the convex section is implemented in plural so as to be multi-stepped.

Fig. 5 shows a longitudinal sectional view of a sound-deadening partition plate of a scroll compressor and its related parts according to a modification of the second embodiment of the present invention, in which the convex section is implemented in plural so as to be multi-stepped.

Detailed Description

The following description of the preferred embodiment(s) is merely exemplary in nature and is in no way intended to limit the utility model, its application, or uses. The same or similar reference numerals are used to designate the same components in the respective drawings, and thus the configurations of the same components will not be described repeatedly.

The basic construction and principles of the scroll compressor 10 will now be described with reference to FIG. 1, it being understood that the muffling construction according to the present invention is applicable to other forms of compressors as well.

As shown in FIG. 1, a scroll compressor 10 includes a generally cylindrical housing 12, a top cover 14 disposed at one end of the housing 12, and a bottom cover 16 disposed at the other end of the housing 12. A cylindrical shell 12, a top cover 14 and a bottom cover 16 form the outer shell of the scroll compressor 10. It should be understood that the housing of the scroll compressor 10 may vary depending on the particular application, and for example, may be closed or may be semi-closed (e.g., omitting the bottom cover 16).

A partition plate 15 for partitioning an internal space of the compressor into a high pressure side and a low pressure side may be provided in a housing of the scroll compressor (also simply referred to as "compressor") 10, particularly between the top cover 14 and the shell 12. The high pressure side is defined between the partition 15 and the top cover 14, and the low pressure side is defined between the partition 15, the housing 12 and the bottom cover 16. An intake joint (not shown) for sucking a working fluid (e.g., refrigerant) is provided at a low pressure side, and a discharge joint for discharging the compressed working fluid is provided at a high pressure side. When the compressor is operated, a low-temperature, low-pressure working fluid enters a low-pressure side of the compressor 10 through an intake joint, is compressed to become a high-temperature, high-pressure working fluid and is discharged to a high-pressure side, and is then discharged out of the compressor 10 through a discharge joint.

A motor 20, a rotary shaft 30, and a compression mechanism are provided in a casing of the compressor 10. The motor 20 is constituted by a stator and a rotor and is configured to drive the rotation shaft 30 to rotate. The rotation shaft 30 is fixedly connected to a rotor of the motor 20. The compression mechanism includes a non-orbiting scroll member 80 and an orbiting scroll member 70. Rotating shaft 30 is configured to drive orbiting scroll member 70 relative to non-orbiting scroll member 80.

Compressor 10 also includes a main bearing housing 40. Main bearing housing 40 is fixedly attached to cylindrical housing 12 and is located within housing 12. Main bearing housing 40 is configured (e.g., may be through a thrust plate) for supporting a compression mechanism, specifically orbiting scroll member 70. The rotary shaft 30 is rotatably supported by a main bearing provided in a main bearing housing 40. A lubricant passage is provided in the rotary shaft 30 to supply lubricant at the bottom cover 16 to the various bearings and other movable parts of the compressor 10.

Orbiting scroll member 70 includes an end plate 72, a hub 74 formed on one side of the end plate, and a helical blade 76 formed on the other side of the end plate. Non-orbiting scroll member 80 includes an end plate 82, a spiral vane 86 formed on one side of the end plate, and a discharge port 88 formed at a substantially central position of the end plate. Wherein the discharge port 88 communicates with an upwardly open recess 89, which recess 89 in turn is in fluid communication with a discharge space (high pressure side) 90 defined by the top cover 14 and the partition 15. An annular recess 92 is formed in non-orbiting scroll member 80. Within this recess 92 is disposed a floating seal assembly. Recesses 89, 92 cooperate with the floating seal assembly to define axial pressure biasing chambers that receive pressurized fluid compressed by vanes 76, 86 to apply an axial biasing force to non-orbiting scroll member 80 to force the tips of each vane 76, 86 into sealing engagement with the opposing end plate surfaces of end plates 72, 82, respectively.

A series of compression chambers of decreasing volume from the radially outer side to the radially inner side are formed between spiral vane 86 of non-orbiting scroll member 80 and spiral vane 76 of orbiting scroll member 70. The radially outermost compression pocket is at suction pressure and the radially innermost compression pocket is at discharge pressure. The intermediate compression chamber is between the suction pressure and the discharge pressure and is therefore also referred to as the intermediate pressure chamber.

One end of the rotating shaft 30 is provided with an eccentric crank pin 36. Eccentric crank pin 36 fits within hub 74 of orbiting scroll member 70. A relief bushing may be disposed between eccentric crank pin 36 and hub 74 of orbiting scroll member 70. When motor 20 is activated, eccentric crank pin 36 of rotatable shaft 30 drives hub 74 of orbiting scroll member 70 such that orbiting scroll member 70 is able to orbit relative to non-orbiting scroll member 80 (i.e., the central axis of orbiting scroll member 70 moves about the central axis of non-orbiting scroll member 80, but orbiting scroll member 70 does not itself rotate about its central axis) to effect compression of the working fluid in the series of compression chambers. The translational rotation is accomplished by an oldham ring (not shown) disposed between non-orbiting scroll member 70 and orbiting scroll member 80.

Next, the noise reduction structure of the compressor will be described still with reference to fig. 1. The noise reduction structure of the compressor may include a partition 15 and an insert 200 installed in the partition, and the fluid compressed by the compression mechanism (the non-orbiting scroll member and the orbiting scroll member) is discharged to the high pressure side 90 through a passage of the insert 200 and then to the outside of the compressor. The insert 200 is mounted in and interference fit with the through hole of the diaphragm 15 to generate a retention force to overcome the downward gas force experienced by the insert based on the pressure differential between the high pressure side and the low pressure side. The disadvantage of this noise reduction structure is that: since the pressure difference between the high pressure side and the low pressure side has a tendency to apply a force downward to the insert (and the valve member provided on the insert), the through hole portion of the partition 15 that is interference-fitted with the insert 200 is enlarged, resulting in a reduction in the holding force for the insert 200 with an increase in the pressure difference, so that the sound-deadening partition holding safety factor and the operational reliability of the compressor are lowered.

A sound deadening structure of a scroll compressor according to an embodiment of the present invention will now be described with reference to fig. 2, and the components having the same reference numerals indicate the same components except for the sound deadening structure.

Fig. 2 shows a longitudinal cross-sectional view of a sound-attenuating partition and its associated components of a scroll compressor in accordance with a first embodiment of the present invention, wherein the sound-attenuating partition is provided with a raised portion in the vicinity of the interference fit of the sound-attenuating partition with the insert, and the sound-attenuating partition further has a main sloped section and a transitional arc portion. In fig. 2, a sound-deadening partition plate 150 of a scroll compressor according to the present invention is used to partition an inner space of the compressor into a high pressure side and a low pressure side, and the sound-deadening partition plate 150 includes a mounting hole 151 and an insert 152 installed in the mounting hole, a fluid compressed by a compression mechanism is discharged to the high pressure side through a passage of the insert 152 and then to the outside of the compressor, the insert 152 is interference-fitted with the mounting hole 151 to have an interference-fitted portion, and a convex section 153 protruding toward the high pressure side direction with respect to the remaining portion of the sound-deadening partition plate is provided at a portion of the sound-deadening partition plate 150 adjacent to the interference-fitted portion. The mounting hole 151 may be provided at the boss section 153.

According to the utility model, the bulge section which is protruded towards the direction of the high pressure side relative to the rest part is arranged at the adjacent part of the insert of the silencing partition plate and the interference fit part of the mounting hole, so that the mounting hole is partially contracted along with the increase of the pressure difference, the holding force on the insert is increased along with the increase of the pressure difference, and the holding safety factor of the silencing partition plate and the operation safety and reliability of the compressor are improved.

Referring again to fig. 2 describing a specific configuration of the sound-attenuating partition, the sound-attenuating partition 150 may have a substantially frustoconical cylindrical shape, the mounting hole 151 may be provided at the center of the sound-attenuating partition, and the sound-attenuating partition further includes a main inclined section 154 and a transition arc portion 155 between the main inclined section 154 and the convex section 153, and the convex section 153 protrudes toward a high pressure side direction with respect to the transition arc portion 155 to have a protrusion height H from a tangent of the transition arc portion.

In one aspect of this embodiment, the protrusion height H may be greater than 1mm and/or the protrusion height H may be less than 5 times the thickness T of the sound-attenuating partition, which may advantageously be selected as the thickness at the transition arcs, or as the average thickness of the sound-attenuating partition.

Wherein the mounting hole 151 may be a circular hole, and generally speaking, for example, when the compressor is at a large displacement, a larger diameter of the circular hole may be beneficial to reduce the pressure difference of the exhaust gas to meet the stability and safety requirements of the compression system. However, a larger diameter of the circular hole may result in a reduction of the safety factor of the sound-dampening construction, because in the case of larger diameters of the circular hole the difference in area on which the high-low pressure difference acts is larger, so that the downward gas force on e.g. the insert is larger, resulting in a loosening of the insert. In contrast, the present invention, including the "raised" feature, allows for a balance between the two, i.e., a reduction in exhaust pressure differential with a larger range of circular hole diameters while maintaining a specified safety factor of the muffling configuration, to meet system stability and safety requirements. In one aspect of the embodiment, the diameter D of the circular hole can be greater than 66mm, and in another aspect of the embodiment, the diameter D of the circular hole can be greater than 50 mm.

In one aspect of this embodiment, the taper angle a of the primary slope section 154 may be greater than 10 ° and less than 60 °.

In an advantageous aspect according to the first embodiment of the present invention, the convex section may be configured as a plurality of connected ones in a multi-step shape. FIG. 4 shows a longitudinal cross-sectional view of the sound-attenuating barrier and its associated components of a scroll compressor according to a variation of the first embodiment of the present invention, in which the raised section 153 of the sound-attenuating barrier 150 "may be configured as a plurality of connected steps.

In terms of space design, the welding stress between the silencing partition plate and the top cover or the shell can be reduced by designing the starting angle of the silencing partition plate to be a larger angle, but the larger angle can cause the gap between the silencing partition plate and the compression mechanism (movable vortex and fixed vortex) to be too large and wastes space, however, the multi-step-shaped convex section according to the utility model can realize the large starting angle of the silencing partition plate relative to the shell, and simultaneously can not cause the large gap between the silencing partition plate and the compression mechanism.

Next, a sound-deadening construction of a scroll compressor according to another embodiment of the present invention will be described with reference to fig. 3, which shows a longitudinal sectional view of a sound-deadening partition plate of a scroll compressor according to a second embodiment of the present invention and its related parts, wherein the sound-deadening partition plate 150' is provided with a convex section in the vicinity of an interference-fit portion of the sound-deadening partition plate with an insert, and the sound-deadening partition plate further has a main inclined section, but the sound-deadening partition plate of the second embodiment does not have a transitional arc portion unlike the first embodiment. The boss section 153 is connected to the main slope section 154, and the boss section 153 includes a boss slope part 153a inclined at a greater taper angle connected to the main slope section 154 and a boss horizontal part 153b extending substantially horizontally from the boss slope part, thereby having a protrusion height H from a connection point of the boss section 153 and the main slope section 154, as viewed in a longitudinal sectional view of the compressor. In one aspect, the protrusion height H may be greater than 1mm, and/or the protrusion height H is less than 5 times the thickness T of the sound-deadening barrier.

In an advantageous aspect according to the second embodiment of the present invention, the convex section may be configured as a plurality of connected ones in a multi-step shape. FIG. 5 shows a longitudinal cross-sectional view of the sound-deadening barrier of a scroll compressor and its related parts according to a modification of the second embodiment of the present invention, wherein the convex section 153 of the sound-deadening barrier 150' "may be constructed in a plurality of stages connected. Similarly to the above-described embodiment, according to the multi-step-shaped convex section of the present invention, a large initial angle of the silencing partition plate with respect to the shell is achieved without causing a large gap between the silencing partition plate and the compression mechanism.

According to an aspect of an embodiment of the present invention, referring to fig. 2 and 3, the insert 152 may be cylindrical and have a bottom wall having a through hole to allow fluid to be discharged to a high pressure side through the insert, and a check valve 160 for selectively opening and closing the through hole is provided at the insert 152. Generally, in the case of an insert provided with a check valve, in particular when the check valve is closed, a reduction in the safety factor of the noise dampening construction may result, because the area difference over which the high-low pressure difference acts when the check valve is closed is large, so that the downward gas force on, for example, the insert is greater, resulting in loosening of the insert. In contrast, the present invention, including the "raised" feature, is applicable to check valves that perform on-off functions while ensuring a specified safety factor of the noise dampening structure. The closing force at this time may be a gas force based on a pressure difference between the high pressure side and the low pressure side to which the insert and the check valve as a whole are subjected. That is, the retention safety factor of the sound-damping partition may be the ratio of the retention force to the gas force based on the pressure differential between the high-pressure side and the low-pressure side to which the insert and the check valve as a whole are subjected.

Advantageously, the sound-attenuating barrier and insert according to the present invention may be configured and adapted (e.g., at maximum differential pressure between low and high chamber pressures, and with a sound-attenuating barrier stress below 314MPa yield strength) such that the insert retention safety factor with respect to the sound-attenuating barrier is greater than 2.0, which is typically 1.1 relative to prior art sound-attenuating barriers. In one embodiment, the retention safety factor may be 2.2.

In yet another advantageous aspect according to an embodiment of the present invention, the compressor may be an inverter scroll compressor.

Although preferred embodiments of the present invention have been described in detail herein, it is to be understood that this invention is not limited to the precise construction herein described and illustrated and that other modifications and variations may be effected by one skilled in the art without departing from the spirit and scope of the utility model. All such modifications and variations are within the scope of the utility model as hereinafter claimed.

Claims (12)

1. A compressor comprising a compression mechanism adapted to compress a fluid and a silencing partition for partitioning an inner space of the compressor into a high pressure side and a low pressure side, the silencing partition comprising a mounting hole and an insert mounted in the mounting hole, a fluid compressed by the compression mechanism being discharged to the high pressure side via a passage of the insert and then to an outside of the compressor,

the insert is in interference fit with the mounting hole to form an interference fit portion, and a protruding portion protruding toward a high-pressure side direction with respect to the rest of the silencing partition plate is provided at a portion of the silencing partition plate adjacent to the interference fit portion.

2. The compressor of claim 1, wherein the mounting hole is provided at the raised section.

3. The compressor of claim 1, wherein the sound-attenuating partition is generally frustoconical in shape, the mounting hole is disposed at a center of the sound-attenuating partition, and the sound-attenuating partition further includes a major angled section.

4. The compressor of claim 3, wherein the taper angle A of the primary slope section is greater than 10 ° and less than 60 °.

5. The compressor of claim 3, wherein the sound-attenuating partition further includes a transition arc portion between the main sloped portion and the convex portion, the convex portion protruding toward a high pressure side direction with respect to the transition arc portion so as to have a protrusion height H starting from a tangent of the transition arc portion.

6. The compressor of claim 3, wherein the raised section is connected to the primary sloped section, the raised section including a raised sloped portion connected to the primary sloped section that slopes at a greater taper angle and a raised horizontal portion extending generally horizontally from the raised sloped portion, thereby having a protrusion height H from a point where the raised section is connected to the primary sloped section.

7. The compressor according to claim 5 or 6, wherein the projection height H is greater than 1mm and/or is less than 5 times the thickness T of the sound-deadening partition.

8. The compressor of claim 5 or 6, wherein the convex section is configured as a plurality of connected ones in a multi-step shape.

9. A compressor according to any one of claims 1 to 6, wherein the mounting hole is a circular hole having a diameter D greater than 50 mm.

10. The compressor of any one of claims 1 to 6, wherein the insert is cylindrical and has a bottom wall with a through hole to allow fluid to be discharged to the high pressure side via the insert, and wherein a check valve for selectively opening and closing the through hole is provided at the insert.

11. The compressor of any one of claims 1 to 6, wherein the sound-attenuating partition and the insert are configured and mated such that a retention safety factor of the insert relative to the sound-attenuating partition is greater than 2.0.

12. The compressor of any one of claims 1 to 6, wherein the compressor is an inverter scroll compressor.

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