WO2014208029A1

WO2014208029A1 - Scroll-type compressor

Info

Publication number: WO2014208029A1
Application number: PCT/JP2014/003106
Authority: WO
Inventors: 俊輔薬師寺; 洋悟高須
Original assignee: 三菱重工業株式会社
Priority date: 2013-06-27
Filing date: 2014-06-11
Publication date: 2014-12-31
Also published as: JP2015010519A; EP3015709A4; EP3015709A1; JP6130748B2; CN105190041B; EP3015709B1; CN105190041A

Abstract

The present invention provides a scroll-type compressor capable of reducing noise of any arbitrary frequency band occurring in the scroll-type compressor. This scroll-type compressor (1) is provided with: a revolving scroll (30) rotatably connected to an eccentric shaft part of a main shaft (17); a stationary scroll (20) facing the revolving scroll (30) to form a compression chamber (PR) for compressing refrigerant, and having an ejection port (23) in a stationary end plate (21), the ejection port being for ejecting compressed refrigerant into a high-pressure chamber (10B); and a discharge cover (25) for covering the ejection port (23). The ejection port (23) comprises an upstream port section (23A) provided on the upstream side of the direction in which refrigerant flows in, and a downstream port section (23B) provided on the downstream side of the direction in which refrigerant flows in, the downstream port section having greater capacity than the upstream port section. Moreover, the downstream port section (23B) is characterized in being provided with a partitioning wall (40) for partitioning the interior thereof into a plurality of areas, and a refrigerant passage whereby the refrigerant passes through the plurality of areas.

Description

Scroll compressor

The present invention relates to a scroll compressor constituting, for example, an indoor air conditioner.

A scroll compressor used in a refrigeration cycle such as an air conditioner or a refrigeration apparatus includes a fixed scroll and a turning scroll. The fixed scroll and the orbiting scroll are each formed by integrally forming a spiral wrap wall on one surface side of a disk-shaped end plate. Such a fixed scroll and the orbiting scroll are made to face each other with the lap wall meshed, and the orbiting scroll is caused to revolve with an electric motor or the like with respect to the fixed scroll. Then, the refrigerant gas in the compression chamber is compressed by reducing the volume while moving the compression chamber formed between both wrap walls from the outer peripheral side to the inner peripheral side.
The refrigerant gas compressed in the compression chamber passes through the discharge port formed in the end plate of the fixed scroll, flows into the high pressure chamber between the discharge cover and the housing, and further from the discharge pipe provided in the housing to the refrigerant circuit. It is discharged toward.

Since the discharge port formed in the fixed scroll affects the performance of the scroll compressor or noise, various proposals have been made.
For example, Patent Document 1 proposes fitting a hollow cylindrical collar to the discharge port in order to suppress vibration and noise due to the discharge of fluid compressed by the turning motion of the scroll. By providing the collar, the excitation force of the in-cylinder pressure pulsation can be reduced, and an increase in compressor noise can be suppressed.

Japanese Utility Model Publication No. 4-82391

However, the vibration and noise generated by the scroll compressor covers a wide frequency range. Therefore, it is difficult to reduce noise in all frequency regions with one noise reduction means. Therefore, it is necessary to take measures according to the frequency to be reduced. For example, since the volume of a discharge port provided with a collar in Patent Document 1 is limited, it is difficult to reduce noise in a low frequency region.
The present invention has been made based on such a technical problem, and an object of the present invention is to provide a scroll compressor that can reduce noise in an arbitrary frequency band generated in the scroll compressor.

By changing the length and volume (hereinafter collectively referred to as the specification) of the discharge port, the resonance frequency at the discharge port can be changed. However, because of the limitations on the size of the scroll compressor, the specification of the discharge port cannot be changed so much, and the resonance frequency cannot be changed.
Therefore, in the present invention, the discharge port provided in the fixed scroll is divided into an upstream port portion and a downstream port portion, and the volume of the downstream port portion is increased to function as a muffler. In addition, by dividing the downstream port part into a plurality of rooms, a resonance frequency different from that of the downstream port part not provided with a partition is realized, thereby reducing sound in an arbitrary frequency band. However, in order for the refrigerant to pass through the downstream port portion without difficulty, a plurality of partitioned rooms need to function as refrigerant passages.

That is, the scroll compressor according to the present invention forms a turning scroll that is rotatably connected to the eccentric shaft portion of the main shaft, a compression chamber that compresses the refrigerant by facing the turning scroll, and the compressed refrigerant is high-pressure. The fixed scroll which has the discharge port which discharges toward a chamber in an end plate, and the discharge cover which covers a discharge port are provided.
In the scroll compressor of the present invention, the discharge port has an upstream port portion provided on the upstream side in the refrigerant inflow direction, and a downstream port portion provided on the downstream side in the refrigerant inflow direction and having a larger volume than the upstream port portion. It consists of. In addition, the downstream port portion includes a partition wall that divides the interior into a plurality of regions, and a refrigerant passage through which the refrigerant passes through the plurality of regions.

The scroll compressor of the present invention is provided with a partition wall at the downstream port portion of the discharge port, and the partition wall can be arbitrarily set in specifications such as length and height. That is, the partition wall can be tuned. Therefore, sound can be reduced in an arbitrary frequency band by tuning the partition wall corresponding to the target scroll compressor.

Generally, the discharge port has a circular inner space (cavity) including the downstream port portion. Assuming this, the partition wall preferably has a circular cross section. This is to reduce the disturbance of the refrigerant flow passing through the downstream port portion. One or more arcuate partition walls can be provided along the circumferential direction of the downstream port portion. In the case of providing a plurality, it is preferable to provide them at mutually symmetrical positions in order to reduce the disturbance of the refrigerant flow.

In the present invention, the method for providing the partition wall is arbitrary, but it is preferably formed integrally with the discharge cover. The discharge cover is manufactured by casting in the same way as the orbiting scroll and fixed scroll. However, if the partition wall is integrally formed by casting, the manufacturing man-hours can be saved compared to the case of separately manufacturing and fixing the partition wall. . In order to increase rigidity, the partition wall is preferably formed integrally with the discharge cover via a rib.

According to the present invention, by providing a partition wall at the downstream port portion of the scroll compressor, the partition wall is tuned to reduce noise in an arbitrary frequency band and suppress noise.

It is a longitudinal section showing a scroll type compressor in this embodiment. (A) is the elements on larger scale near the discharge port of the fixed scroll of FIG. 1, (b) is a perspective view which shows typically the discharge port vicinity of (a). (A)-(f) is a cross-sectional view for demonstrating the various installation states of a partition wall. (A)-(c) is a cross-sectional view for demonstrating the handwork which improves the rigidity of a partition wall. It is a figure which shows the effect of the sound reduction in this embodiment.

Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.
As shown in FIG. 1, the scroll compressor 1 of this embodiment includes an electric motor 12 and a scroll compression mechanism 2 driven by the electric motor 12 in a housing 10. The scroll compressor 1 compresses refrigerant such as R410C and R407C and supplies the compressed refrigerant to a refrigerant circuit such as an air conditioner or a refrigerator. Hereinafter, the configuration of the scroll compressor 1 will be described.

The housing 10 includes a bottomed cylindrical housing main body 101 having an open upper end, and a housing top 102 that covers an opening at the upper end of the housing main body 101.
A suction pipe 13 for introducing a refrigerant into the housing body 101 from an accumulator (not shown) is provided on a side surface of the housing body 101.
The housing top 102 is provided with a discharge pipe 14 that discharges the refrigerant compressed by the scroll compression mechanism 2. The interior of the housing 10 is partitioned into a low pressure chamber 10A and a high pressure chamber 10B by a discharge cover 25.

The electric motor 12 includes a stator 15 and a rotor 16.
The stator 15 is provided with a winding that generates a magnetic field when electric power is supplied through a power supply unit (not shown) attached to the side surface of the housing body 101. The rotor 16 includes a permanent magnet and a yoke as main elements, and a main shaft 17 is integrally coupled around the center.

An upper bearing 18 and a lower bearing 19 that rotatably support the main shaft 17 are provided on both ends of the main shaft 17 with the electric motor 12 interposed therebetween.
In the accommodation space 190 formed in the upper bearing 18, an eccentric pin 17A provided at the upper end of the main shaft 17 protrudes and is accommodated.

The scroll compression mechanism 2 includes a fixed scroll 20 and a turning scroll 30 that revolves with respect to the fixed scroll 20.
The fixed scroll 20 includes a fixed end plate 21 and a spiral wrap 22 erected from one surface of the fixed end plate 21. The fixed scroll 20 is also provided with a discharge port 23 in the fixed end plate 21.
As shown in FIG. 2A, the discharge port 23 has an upstream port portion 23A having a circular opening shape (cavity) and a downstream port having a volume larger than that of the upstream port portion 23A. Part 23B. The upstream port portion 23A is disposed on the upstream side in the refrigerant flow direction A, and the downstream port portion 23B is disposed on the downstream side. By increasing the opening area of the downstream port portion 23B located on the downstream side in the direction A, the pressure loss of the refrigerant in the portion can be reduced. 2B shows only the vicinity of the downstream end portion 23B of the fixed end plate 21 in a state where the discharge cover 25 is removed. The same applies to FIGS. 3A to 3F described later.
The upstream port portion 23 A communicates with a compression chamber PR formed between the fixed scroll 20 and the orbiting scroll 30 on the upstream side. Further, the downstream port portion 23 B communicates with the discharge port 27 of the discharge cover 25 that covers the upper side of the fixed scroll 20 on the downstream side.

A partition wall 40 is provided in the downstream port portion 23B. The partition wall 40 is composed of

partition walls

40a and 40b having the same shape and the same dimensions, each of which has an arcuate cross section.
The partition wall 40 partitions the downstream port portion 23B into the outer region OA and the inner region IA, and changes the natural frequency of the downstream port portion 23B. The

partition walls

40a and 40b are disposed at symmetrical positions around the center C of the downstream port portion 23B. By disposing the partition wall 40 at a symmetrical position, it is possible to reduce disturbance of the refrigerant flow in the downstream port portion 23B. A gap G is provided between the circumferential ends E of the

partition walls

40a and 40b. The gap G is provided over the entire area of the

partition walls

40a and 40b in the height direction, and communicates the outer region OA and the inner region IA in the radial direction. The refrigerant that has flowed into the downstream port portion 23B flows into the discharge port 27 of the discharge cover 25 through the refrigerant passage that continues to the outer region OA, the gap G, and the inner region IA.
The partition wall 40 is formed integrally with the discharge cover 25, and is provided so that the tip thereof is in contact with the surface of the fixed end plate 21.
The operation and effect of providing the partition wall 40 will be described later.

The orbiting scroll 30 is also provided with a disc-shaped orbiting end plate 31 and a spiral wrap 32 erected from one surface of the orbiting end plate 31.
A boss 34 is provided on the rear surface of the orbiting end plate 31 of the orbiting scroll 30, and a drive bush 36 is assembled to the boss 34 via a bearing. An eccentric pin 17A is fitted inside the drive bush 36. As a result, the orbiting scroll 30 is eccentrically coupled to the axis of the main shaft 17. Therefore, when the main shaft 17 rotates, the orbiting scroll 30 rotates (revolves) with the eccentric distance from the axis of the main shaft 17 as the orbiting radius.
An Oldham ring (not shown) that restrains rotation is provided between the orbiting scroll 30 and the main shaft 17 so that the orbiting scroll 30 does not rotate while revolving.

The wraps 22 and 32 that are eccentric with each other by a predetermined amount and meshed with a phase difference of 180 degrees contact each other at a plurality of locations according to the rotation angle of the orbiting scroll 30. Then, the compression chamber PR is formed point-symmetrically with respect to the spiral center portions (innermost peripheral portions) of the

wraps

22 and 32, and the compression chamber reduces its volume as the orbiting scroll 30 turns. Gradually moved to the inner circumference. The refrigerant is compressed to the maximum at the center of the spiral. The compression chamber PR in FIG. 1 shows this portion.

In this scroll type compression mechanism 2, the volume of the compression chamber PR formed between the

scrolls

20 and 30 is also reduced in the wrap height direction in the middle of the spiral. Therefore, in both the fixed scroll 20 and the orbiting scroll 30, the height of the wrap is made lower on the inner peripheral side than on the outer peripheral side, and the other end plate facing the stepped wrap is placed on the inner side from the outer peripheral side. On the circumferential side, it protrudes toward the inner surface of the end plate.

In order to start the scroll compressor 1 having the above configuration, the electric motor 12 is excited and a refrigerant is introduced into the housing 10 through the suction pipe 13.
When the electric motor 12 is energized, the main shaft 17 rotates, and the orbiting scroll 30 revolves with respect to the fixed scroll 20 accordingly. Then, the refrigerant is compressed in the compression chamber PR between the orbiting scroll 30 and the fixed scroll 20, and the refrigerant introduced into the low pressure chamber 10 A in the housing 10 from the suction pipe 13 is exchanged between the orbiting scroll 30 and the fixed scroll 20. Inhaled in between. Then, the refrigerant compressed in the compression chamber PR sequentially passes through the discharge port 23 of the fixed end plate 21 and the discharge port 27 of the discharge cover 25 and is discharged to the high pressure chamber 10B, and further discharged from the discharge pipe 14 to the outside. Is done. In this way, refrigerant suction, compression, and discharge are continuously performed.

[Action / Effect]
Next, the operation and effect by providing the partition wall 40 in the downstream port portion 23B will be described.
The refrigerant compressed by the fixed scroll 20 and the orbiting scroll 30 is discharged from the compression chamber PR to the upstream port portion 23A, and sequentially passes through the upstream port portion 23A and the downstream port portion 23B. The refrigerant that has passed through the downstream port portion 23B is discharged from the discharge port 27 to the high-pressure chamber 10B.
The refrigerant discharged into the high pressure chamber 10B through this path causes resonance at a frequency corresponding to each discharge port. When resonance occurs, the amplitude of the discharge port increases rapidly, resulting in increased noise.
Therefore, in the present embodiment, the partition wall 40 is provided in the downstream port portion 23B, thereby partitioning the internal space of the downstream port portion 23B into the outer region OA and the inner region IA. By doing so, the natural frequency in the downstream port portion 23B is changed when the partition wall 40 is not provided. By changing the natural frequency in this way, it is possible to reduce sound in an arbitrary frequency band.

Here, in the present embodiment, an arbitrary frequency band can be reduced by setting the length L of the partition wall 40 to ½ of the wavelength λ of the sound to be reduced.
The principle of reducing the sound of an arbitrary frequency is as follows.
In general, the following relationship (Equation 1) holds among the sound velocity c, the frequency f, and the wavelength λ.
c [m / s] = f [Hz] × λ [m] (Formula 1)
(C: speed of sound, f: frequency, λ: wavelength)
If the frequency f to be reduced is determined, the wavelength λ can be calculated from the equation (1). Then, ½ of the calculated wavelength λ is set as the length L of the partition wall 40.
In addition, as the length L of the partition wall 40 is increased, the low frequency sound can be reduced. On the contrary, as the length of the partition wall 40 is decreased, the high frequency sound tends to be reduced. However, not only the length L but also the height T of the partition wall 40 is an object of tuning of the partition wall 40.

In order to confirm the effect of this embodiment, the relationship between the frequency and the volume reduction was examined for both the compressor provided with the partition wall 40 and the compressor not provided with the partition wall 40. The result is shown in FIG. The vertical axis represents the volume reduction, and the larger the value, the greater the amount of sound reduction.
As shown in FIG. 5, for example, it has been found that by providing the partition wall 40 in a frequency band of 1.6 kHz, it is possible to reduce sound by about 25 dB. Similarly, by providing the partition wall 40, it has been found that sound reduction can be promoted even in the frequency band of 4.0 to 5.0 kHz.
From the above results, it was confirmed that by providing the partition wall 40 in the downstream port portion 23B, it is possible to reduce the sound corresponding to 1.6 kHz and 4.1 kHz that cause noise.

[Example of partition wall shape]
In the above, an example in which two

partition walls

40a and 40b having the same shape and the same size are provided symmetrically has been described. However, the present invention is not limited to this, and various modifications can be made to the formation pattern of the partition wall 40. it can. With reference to FIG. 3, some examples are shown.
For example, one gap G of the

partition walls

40a and 40b can be connected to form a C-shaped partition wall 40 as shown in FIG. Thus, by increasing the length L of the arc of the partition wall 40, it is possible to reduce the sound of a lower frequency.
Moreover, as shown in FIG.3 (b), the symmetrical center C 'of the partition wall 40 (40a, 40b) can also be provided in the position eccentric from the center C of the downstream port part 23B.
Moreover, as shown in FIG.3 (c), the

partition walls

40a and 40b from which the length of an arc differs can be used. By doing so, the sound of the frequency of a different area | region can be reduced, respectively. In this case, as shown in FIG.3 (c), the distance from the center C to the

partition walls

40a and 40b can be varied.
Moreover, as shown in FIG.3 (d), the partition wall 40 can also be divided and provided in three or more (three in FIG.3 (d)). By providing a large number of partition walls 40, the sound reduction effect can be increased.
Moreover, as shown in FIG.3 (e), the

partition walls

40a, 40c, 40b, and 40d can also be provided in double in the radial direction. Also in this case, the downstream port portion 23B is partitioned into a plurality of regions. That is, each of the partition walls 40a to 40d is partitioned into a radially inner region and an outer region.
This is effective when the arc length L of the partition wall 40 as a whole is increased to increase the sound reduction effect. It should be noted that the partition wall 40 is not limited to being double, and the partition wall 40 may be triple or more.
Furthermore, as shown in FIG. 3 (f), the partition wall 40 may be spiral. The spiral partition wall 40 partitions the downstream port portion 23 B into an inner area surrounded by the partition wall 40 in the radial direction and an outermost outermost area of the partition wall 40.
Even when the partition wall 40 is formed in a spiral shape, the length L of the partition wall 40 can be increased, which is effective in reducing the sound of a lower frequency.
The refrigerant flowing in from the upstream port portion 23A passes through the downstream port portion 23B while flowing in a spiral shape along the partition wall 40, and is discharged to the discharge port 27.
It should be noted that the forms shown in FIGS. 3A to 3F can be appropriately combined.
In addition, the partition wall 40 is not limited to an arc shape (or an elliptical arc shape), and various types of partition walls 40 such as a linear shape or a U-shape may be used. Further, when a plurality of, for example, two

partition walls

40a and 40b are provided, they can be provided at asymmetric positions. In short, the form of the partition wall is not limited as long as the partition wall is tuned according to the frequency band to be reduced.

[Example of improved rigidity]
Next, the partition wall 40 needs to have rigidity that can counteract the pressure received from the refrigerant passing through the discharge port 23. The rigidity referred to here is exclusively related to the joint portion with the discharge cover 25.
Therefore, in the present embodiment, as shown in FIG. 4A, ribs 41 projecting outward in the radial direction can be provided at the end portions E and E of the

partition walls

40a and 40b. By providing the rib 41, the

partition walls

40a and 40b are improved in rigidity against the pressure of the refrigerant from the inner region IA toward the outer side in the radial direction. The rib 41 has the same height as the partition wall 40 and has a uniform width in the height direction, but is not limited to this as long as the effect of improving the rigidity can be obtained.
The rib 41 has a function of forming a diaphragm in addition to a function of improving rigidity. That is, by providing the rib 41, the refrigerant inlet / outlet 44 from the inner area IA to the outer area OA is throttled, so that the effect of reducing sound is increased.

In addition to the rib 41, as shown in FIG. 4 (b), the rib 42 can be provided at an arbitrary position between the end portions E and E, for example, at an intermediate position. By doing so, the rigidity of the partition wall 40 is further improved, and the partition wall 50 having a length of 1/2 L is formed between the rib 41 and the rib 42, so that the sound in the high frequency range is also reduced. I can sound.

In order to improve rigidity, a partition wall 43 having a corrugated cross section can also be applied as shown in FIG. In the partition wall 43, portions corresponding to the corrugated peaks and valleys exhibit the same action as the rib 41. Moreover, since there are a plurality of these portions, the partition wall 43 has higher rigidity.

The embodiment has been described above. In addition to the above, the configuration described in the above embodiment can be selected or changed to another configuration as appropriate without departing from the gist of the present invention.
For example, the partition wall 40 is not limited to be formed integrally with the discharge cover 25 as long as the downstream port portion 23B is partitioned into the outer region OA and the inner region IA. For example, it may be formed integrally with the fixed end plate 21, or may be manufactured separately from the fixed end plate 21 and the discharge cover 25 and fixed to a predetermined position of the downstream port portion 23 B by an appropriate means.

Furthermore, the tip of the partition wall 40 is not necessarily in contact with the fixed end plate 21, and the tip of the partition wall 40 may be separated from the fixed end plate 21 as long as the sound reduction effect by the partition wall is obtained.

DESCRIPTION OF SYMBOLS 1 Scroll type compressor 2 Scroll type compression mechanism 10 Housing 10A Low pressure chamber 10B High pressure chamber 12 Electric motor 13 Suction pipe 14 Discharge pipe 15 Stator 16 Rotor 17 Main shaft 17A Eccentric pin 18 Upper bearing 19 Lower bearing 20 Fixed scroll 21

Fixed end plate

22 , 32 Lap 23 Discharge port 23A Upstream port portion 23B Downstream port portion 25 Discharge cover 27 Discharge port 30 Revolving scroll 31 Revolving end plate 34 Boss 36

Drive bushes

40, 40a to 40d, 43

Partition walls

41, 42 Rib 44 Entrance / exit 101 Housing body 102 Housing top 190 Accommodating space A Orientation OA Outside area IA Inside area C, C ′ Center G Gap PR Compression chamber

Claims

An orbiting scroll rotatably connected to the eccentric shaft portion of the main shaft,
A fixed scroll that forms a compression chamber for compressing the refrigerant by facing the orbiting scroll, and has a discharge port for discharging the compressed refrigerant toward the high-pressure chamber on an end plate;
A discharge cover covering the discharge port;
With
The discharge port is
An upstream port portion provided on the upstream side in the refrigerant inflow direction, and a downstream port portion provided on the downstream side in the refrigerant inflow direction and having a larger volume than the upstream port portion,
The downstream port portion is
A partition wall that divides the interior into a plurality of regions;
And a refrigerant passage through which the refrigerant passes through the plurality of regions.
The downstream port portion has a circular cavity.
The partition wall having an arc-shaped cross section is provided singly or plurally along the circumferential direction of the downstream port portion.
The scroll compressor according to claim 1.
The partition wall is
Formed integrally with the discharge cover,
The scroll compressor according to claim 1 or 2, characterized by the above-mentioned.
The partition wall is
Formed integrally with the discharge cover via a rib,
The scroll compressor according to any one of claims 1 to 3, wherein
The partition wall is
The tip is provided so as to contact the surface of the end plate,
The scroll compressor according to any one of claims 1 to 4, wherein the scroll compressor is provided.
The partition wall is
Centered on the central part of the downstream port part, it is arranged at a symmetrical position,
The scroll compressor according to any one of claims 1 to 5, wherein:
The partition wall is
Centered on the position eccentric from the central part of the downstream port part, it is arranged at a symmetrical position,
The scroll compressor according to any one of claims 1 to 5, wherein: