WO2013065706A1

WO2013065706A1 - Sealed rotary compressor and refrigeration cycle device

Info

Publication number: WO2013065706A1
Application number: PCT/JP2012/078100
Authority: WO
Inventors: 加藤　久尊; 明森嶋; 健富永; 大志長畑; 平山　卓也
Original assignee: 東芝キヤリア株式会社
Priority date: 2011-10-31
Filing date: 2012-10-31
Publication date: 2013-05-10
Also published as: JPWO2013065706A1; CN103906928B; CN103906928A; JP5786030B2

Abstract

With a sealed rotary compressor of an embodiment of the present invention, when the total cross-sectional area of connecting passages that are provided from an auxiliary bearing to a main bearing and that enable high-pressure gas within a second muffler to converge with high-pressure gas within a first muffler is S1 [mm²], and the total surface area of a sealed-case-internal discharge part which is provided on the first muffler is S2 [mm²], S2 is set so as to be greater than S1 (S1 < S2), and when the distance from one end surface of the stator in an electric motor unit to one end surface of the sealed case is A and the distance from the other end of the stator to the other end of a member (for example, a first cylinder) which fastens a compression mechanism unit to the sealed case is B, then 0.5 < B/A < 1 . . . (1).

Description

Hermetic rotary compressor and refrigeration cycle equipment

Embodiments of the present invention relate to a hermetic rotary compressor having one or two cylinders, and a refrigeration cycle apparatus that includes this hermetic rotary compressor and constitutes a refrigeration cycle.

A hermetic rotary compressor having one or two cylinders accommodates a compression mechanism part in the lower part of the hermetic case, and accommodates an electric motor part connected to the compression mechanism part via a rotating shaft at the upper part of the compression mechanism part. Do it.

In the compression mechanism section, the gas refrigerant is compressed in the cylinder chamber to increase the pressure. The high-pressure gas refrigerant is discharged to the first muffler via the first discharge valve mechanism provided in the main bearing and then discharged into the sealed case. The high-pressure gas refrigerant is temporarily discharged from the cylinder chamber to the second muffler via a second discharge valve mechanism provided in the sub bearing.

Since the second muffler communicates with the first muffler via a communication path provided in the sub-bearing, the cylinder and the main bearing, the gas refrigerant is mixed in the first muffler and then placed in the sealed case. Released.

Japanese Patent No. 3300322

In this hermetic rotary compressor, the opening area of the discharge part in the hermetic case, which is the opening in the first muffler, is made as small as possible to obtain a silencing effect. On the other hand, the total cross-sectional area of the communication path is formed as large as possible so that the gas refrigerant can be guided smoothly.

There is no problem in the region where the operating frequency of the compressor is low, but in the region where the operating frequency is high, the passage resistance (flow path loss) when discharged from the first muffler into the sealed case becomes large, and the cylinder chamber Then it becomes overcompressed. Therefore, when the compressor is rotated at a high speed and exhibits a high capacity, the flow rate of the gas refrigerant is increased, so that the passage resistance is greatly increased.

For this reason, the gas refrigerant discharged from the discharge part in the sealed case of the first muffler provided in the main bearing is discharged into the sealed case without increasing the noise and without increasing the passage resistance. There is a demand for a hermetic rotary compressor that can be used, and a refrigeration cycle apparatus including the hermetic rotary compressor.

In this embodiment, a hermetic rotary compressor in which a compression mechanism portion is housed in a lower portion in a hermetically sealed case, an electric motor portion is housed in an upper portion, and the motor portion is connected to the compression mechanism portion via a rotating shaft. The compression mechanism section includes one cylinder or two cylinders having an inner diameter portion as a cylinder chamber, a main bearing and a sub-bearing that pivotally support the rotating shaft, and a main bearing and a sub-bearing, respectively. A first discharge valve mechanism and a second discharge valve mechanism that are provided and discharge and guide the high-pressure gas compressed in the cylinder chamber, and cover the first discharge valve mechanism and receive the high-pressure gas once compressed in the cylinder chamber Then, the first muffler discharged into the sealed case through the discharge part in the sealed case and the second discharge valve mechanism are covered, and the gas refrigerant once compressed in the cylinder chamber is received and silenced. Do 2 mufflers and a communication passage provided from the sub bearing to the main bearing for guiding the gas refrigerant in the second muffler and joining the gas refrigerant in the first muffler. When the sectional area is S1 [mm ² ] and the total area of the discharge part in the sealed case provided in the first muffler is S2 [mm ² ], S2 is larger than S1 (S1 <S2), and the electric motor part Comprises a stator that is inserted into a sealed case, and a rotor that is fitted to a rotating shaft and has an outer peripheral wall provided with a narrow gap from the inner peripheral wall of the stator. (1) where A is the dimension from the upper end surface to the one end surface of the sealed case and B is the distance from the lower end surface of the stator core to the end surface of the member that fixes the compression mechanism to the sealed case. It is set to satisfy the formula.
0.5 <B / A <1 (1)
Further, the refrigeration cycle apparatus of the present embodiment configures a refrigeration cycle by communicating the hermetic rotary compressor, the condenser, the expansion device, and the evaporator via a refrigerant pipe.

FIG. 1 is a longitudinal sectional view and a refrigeration cycle configuration diagram of a two-cylinder hermetic rotary compressor according to a first embodiment. FIG. 2 is a longitudinal sectional view and a refrigeration cycle configuration diagram of the one-cylinder hermetic rotary compressor according to the embodiment. FIG. 3 is a plan view of the main bearing according to the embodiment. FIG. 4 is a plan view of the cylinder according to the embodiment. FIG. 5 is a diagram illustrating the magnitude of noise under different conditions according to the embodiment. FIG. 6 is a change diagram of the pressure loss when the ratio of the excluded volume V2 of the cylinder chamber and the total area S2 of the discharge part in the sealed case in the first muffler is changed according to the embodiment. FIG. 7A is a plan view of a cylinder showing a discharge notch according to the second embodiment. FIG. 7B is a longitudinal sectional view of a cylinder showing a discharge notch according to the embodiment. FIG. 8 is a partial perspective view of a cylinder showing a discharge notch according to the embodiment. FIG. 9 is a longitudinal sectional view of a cylinder showing a discharge notch according to the third embodiment. FIG. 10 is a partial perspective view of a cylinder showing a discharge notch according to the embodiment. FIG. 11 is a plan view showing the first muffler according to the first embodiment. FIG. 12 is a plan view showing a first muffler according to the fourth embodiment. FIG. 13 is a plan view showing a first muffler according to the fifth embodiment.

Hereinafter, the present embodiment will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view and a refrigeration cycle configuration diagram of a hermetic rotary compressor 1 and an accumulator 5 used in the refrigeration cycle apparatus R.

1 in the figure is a hermetic rotary compressor 1 described later. The hermetic rotary compressor 1 is hereinafter referred to as a compressor 1. A refrigerant pipe P is connected to the upper end portion of the compressor 1. In the refrigerant pipe P, a condenser 2, an expansion valve (expansion device) 3, an evaporator 4 and an accumulator 5 are sequentially provided. Further, the refrigerant pipe P branches from the accumulator 5 into two refrigerant pipes Pa and Pb, and is connected to the side portion of the compressor 1. These constitute a refrigeration cycle apparatus R such as an air conditioner.

Next, the compressor 1 will be described.
The compressor 1 includes a sealed case 10. The electric motor part 11 is accommodated in the upper part inside the sealed case 10 and the compression mechanism part 12 is accommodated in the lower part. The electric motor unit 11 and the compression mechanism unit 12 are integrally connected via a rotating shaft 13.

An oil reservoir 14 for collecting lubricating oil is formed at the inner bottom of the sealed case 10. Almost most of the compression mechanism 12 disposed on the lower side is immersed in the lubricating oil.

The electric motor unit 11 includes a rotor (rotor) 15 fitted and fixed to the rotary shaft 13 and a stator (stator) 16. The stator 16 is opposed to the inner peripheral wall of the outer peripheral wall of the rotor 15 with a narrow gap, and the outer peripheral wall is fitted and fixed to the inner peripheral wall of the sealed case 10.

Here, the compression mechanism section 12 is of a two-cylinder type.
The first cylinder 17A has an inner diameter portion along the central axis. The first cylinder 17 </ b> A has an outer peripheral wall inserted into the inner peripheral wall of the sealed case 10, and is attached and fixed by means such as partial welding. The main bearing 18 is placed on the upper surface portion of the first cylinder 17A. The main bearing 18 closes the upper surface side of the inner diameter portion of the first cylinder 17A.

The first muffler 19 is mounted on the main bearing 18. The main bearing 18 and the first muffler 19 are attached and fixed to the first cylinder 17A via an attachment. On the lower surface portion of the first cylinder 17A, an intermediate partition plate 20, a second cylinder 17B, a sub bearing 21 and a second muffler 22 are attached and fixed to the first cylinder 17A via attachments. .

The intermediate partition plate 20 closes the lower surface side of the inner diameter portion of the first cylinder 17A. The inner diameter portion of the first cylinder 17A closed by the intermediate partition plate 20 and the main bearing 18 is referred to as a first cylinder chamber D1.

The second cylinder 17B has an inner diameter part having the same size and shape as the inner diameter part of the first cylinder 17A, and the upper surface side of the inner diameter part is closed by the intermediate partition plate 20. The sub bearing 21 closes the lower surface side of the inner diameter portion of the second cylinder 17B. The inner diameter portion of the second cylinder 17B closed by the intermediate partition plate 20 and the auxiliary bearing 21 is referred to as a second cylinder chamber D2.

The rotating shaft 13 protrudes downward from the lower end surface of the rotor 15 constituting the electric motor unit 11. The rotary shaft 13 passes through the main bearing 18, the first cylinder chamber D 1, the intermediate partition plate 20, the second cylinder chamber D 2, and the auxiliary bearing 21 that constitute the compression mechanism portion 12. In particular, the upper part of the rotating shaft 13 protruding from the first cylinder chamber D1 is pivotally supported by the main bearing 18, and the lower part of the rotating shaft 13 protruding from the second cylinder chamber D2 rotates to the auxiliary bearing 21. It is supported freely.

Further, the rotating shaft 13 is integrally provided with a first eccentric portion 13a and a second eccentric portion 13b formed with a phase difference of about 180 ° in the first cylinder chamber D1 and the second cylinder chamber D2. Yes. The eccentric parts 13a and 13b have the same diameter, and their central axes are eccentric by a predetermined amount.

The first roller 23a is fitted to the circumferential surface of the first eccentric portion 13a, and the second roller 23b is fitted to the circumferential surface of the second eccentric portion 13b. When the rotary shaft 13 rotates, the first and

second rollers

23a and 23b are assembled so as to be able to rotate while making line contact with a part of the inner peripheral walls of the first and second cylinder chambers D1 and D2, respectively.

The first blade back chamber communicates with the first cylinder chamber D1 of the first cylinder 17A through the blade groove. The blade groove is not shown here. same as below. A first blade is movably accommodated in the blade groove. A second blade back chamber communicates with the second cylinder chamber D2 of the second cylinder 17B via a blade groove. A second blade is movably accommodated in the blade groove.

The tip portions of the first and second blades are formed in a substantially arc shape in plan view and can protrude into the opposing cylinder chambers D1 and D2. In this state, the tip of the blade makes line contact with the peripheral walls of the first and

second rollers

23a and 23b that are circular in plan view regardless of the rotation angle.

A spring member for applying an elastic force acting as a back pressure on the first blade is accommodated between the rear end portion of the first blade and the peripheral wall of the first blade back chamber. A spring member for applying an elastic force acting as a back pressure on the second blade is accommodated between the second blade rear end portion and the second blade back chamber peripheral wall.

Further, in the first cylinder 17A, a first discharge notch described later is provided in the vicinity of one side of the blade groove. The first discharge notch will be described with reference to FIGS. And the 1st suction hole is provided in the site | part on the opposite side to the 1st notch for discharge with respect to a blade groove | channel.

The first suction hole is provided so as to penetrate from the part of the outer peripheral surface of the first cylinder 17 </ b> A to the first cylinder chamber D <b> 1 and protrudes from the lower end surface of the accumulator 5. Is connected through the sealed case 10.

In the second cylinder 17B, a second discharge notch is provided near one side of the blade groove. And the 2nd suction hole is provided in the site | part on the opposite side to the 2nd notch for discharge with respect to a blade groove | channel.

The second suction hole is provided so as to penetrate from the part of the outer peripheral surface of the second cylinder 17B to the second cylinder chamber D2, and the other refrigerant pipe Pb protruding from the lower end surface of the accumulator 5 is provided. Is connected through the sealed case 10.

A first discharge hole 25a is provided in a portion of the main bearing 18 facing the first discharge notch. The first discharge hole 25a is opened and closed by a first discharge valve mechanism 26a attached to the main bearing 18. That is, the first discharge valve mechanism 26a is only in the first discharge hole 25a only when a pressure equal to or higher than a predetermined pressure is applied to the first discharge valve mechanism 26a from the first discharge notch and the first discharge hole 25a. Is opened and the others are closed.

The first discharge valve mechanism 26 a is covered with a first muffler 19 attached to the main bearing 18. The first muffler 19 includes a sealed case discharge portion 28 that opens into the sealed case 10. FIG. 11 is a plan view showing the first muffler 19. As shown in FIG. 11, the in-sealed case discharge portion 28 may be opened at a part of the peripheral surface of the first muffler 19. In the present embodiment, the planar shape of the discharge part 28 in the sealed case is a round hole as an example.

In the sub-bearing 21, a second discharge hole 25b is provided at a portion facing the second discharge notch. The second discharge hole 25b is opened and closed by a second discharge valve mechanism 26b provided in the auxiliary bearing 21.

In other words, the second discharge valve mechanism 26b is connected to the second discharge hole 25b only when a pressure equal to or higher than a predetermined pressure is applied to the second discharge valve mechanism 26b from the second discharge notch and the second discharge hole 25b. Is opened and the others are closed. The second discharge valve mechanism 26 b is covered with the second muffler 22 attached to the sub bearing 21.

The second muffler 22 does not include the discharge part 28 in the sealed case that opens into the sealed case 10 like the first muffler 19 and has a sealed structure. However, the second muffler 22 opens with respect to the communication path 30 described later. The communication passage 30 has a large width for easy viewing.

The communication passage 30 has a hole shape provided from the flange portion of the auxiliary bearing 21 to the second cylinder 17B, the intermediate partition plate 20, the flange portions of the first cylinder 17A and the main bearing 18.

The one end part of the communication path 30 opens in the flange part of the sub bearing 21, so that the communication path 30 communicates with the inside of the second muffler 22. Further, the other end portion of the communication passage 30 opens in the flange portion of the main bearing 18, so that the communication passage 30 communicates with the inside of the first muffler 19.

Next, the compression action of the hermetic rotary compressor 1 and the refrigeration action of the refrigeration cycle apparatus R will be described.
When the compressor 1 is energized, a rotating magnetic field is generated in the stator 16 of the electric motor unit 11, thereby rotating the rotor 15 and rotating the rotating shaft 13. A driving torque acts on the compression mechanism portion 12 via the rotation shaft 13, and the first eccentric portion a and the second eccentric portion b of the rotation shaft 13, and the first roller 23a and the second roller 23b are integrated. The eccentric motion is performed in the first cylinder chamber D1 and the second cylinder chamber D2.

The first and second blades receive the back pressure of the spring member, and the tip portions protrude into the cylinder chambers D1 and D2 and retract and immerse. The leading edges of the first and second blades are always in contact with the outer peripheral surfaces of the first and

second rollers

23a and 23b, so that each blade has a suction chamber and a first and second cylinder chambers D1 and D2, respectively. It is divided into two chambers, the compression chamber.

As each

roller

23a, 23b is driven with a phase difference of 180 °, the volume of the suction chamber gradually increases, while the volume of the compression chamber gradually decreases, and the gas refrigerant in the compression chamber is compressed. As a result, the gas refrigerant becomes a predetermined high pressure state and becomes high temperature.

The high-temperature and high-pressure gas refrigerant is opened by applying a predetermined pressure to the first and second

discharge valve mechanisms

26a and 26b through the discharge notches and the first and second discharge holes 25a and 25b. The gas refrigerant in the first cylinder chamber D1 is discharged into the first muffler 19 and is temporarily stored inside. After that, it is discharged into the sealed case 10 through the discharge part 28 in the sealed case provided in the first muffler 19 and fills here.

On the other hand, the gas refrigerant is discharged into the second muffler 22 in the second cylinder chamber D2, and is temporarily stored inside. After that, the gas refrigerant is guided to the communication passage 30 provided in the flange portion of the sub-bearing 21 and passes through the second cylinder 17B, the intermediate partition plate 20, the first cylinder 17A and the flange portion of the main bearing 18. Then, it is guided into the first muffler 19.

The high-temperature and high-pressure gas refrigerant discharged from the first cylinder chamber D1 into the first muffler 19 is already linked to the high-temperature and high-pressure gas refrigerant discharged from the second cylinder chamber D2 into the second muffler 22. It is guided through the passage 30 and joins in the first muffler 19. The merged gas refrigerant is discharged into the sealed case 10 from a sealed case discharge portion 28 provided in the first muffler 19.

The high-temperature and high-pressure gas refrigerant that fills the sealed case 10 is guided to the upper part of the sealed case 10 via a gas guide path provided along the axial direction of the electric motor unit 11, and is further discharged to the refrigerant pipe P. The gas refrigerant is guided to the condenser 2 to exchange heat with the outside air or water, and is condensed and liquefied to be converted into a liquid refrigerant. The liquid refrigerant is adiabatically expanded by the expansion valve 3 and is evaporated by exchanging heat with the surrounding air by the evaporator 4.

At this time, as the refrigerant evaporates, it takes away latent heat of vaporization from the surrounding area and converts it into cold air, thereby performing a freezing action on the surrounding area. The refrigerant evaporated in the evaporator 4 is guided to the accumulator 5 and separated into gas and liquid. Then, the refrigerant is sucked into the first cylinder chamber D1 and the second cylinder chamber D2 of the compressor 1, and is compressed again to be converted into a high-temperature and high-pressure gas refrigerant, and the above-described refrigeration cycle is repeated.

FIG. 2 is a longitudinal sectional view of a single cylinder type hermetic rotary compressor 1A and a refrigeration cycle configuration diagram of the refrigeration cycle apparatus R. The same components of the two-cylinder sealed rotary compressor 1 and the refrigeration cycle apparatus R shown in FIG.

The difference from the two-cylinder type hermetic rotary compressor 1 is that the cylinder 17 is single, the inner bearing is closed from the upper surface by the main bearing 18, and the auxiliary bearing 21 is closed from the lower surface. This is the point where D is formed. A discharge notch is provided at the same position on the upper and lower surfaces of the cylinder chamber D.

That is, a discharge notch is provided in the upper part of the cylinder chamber D, the first discharge hole 25a provided in the main bearing 18 faces the discharge notch, and the first discharge hole 25a is used as the first discharge hole. The valve mechanism 26a opens and closes. A discharge notch is provided in the lower part of the cylinder chamber D, a second discharge hole 25b provided in the sub-bearing 21 is opposed to the discharge notch, and the second discharge hole 25b is used as a second discharge valve mechanism. 26b opens and closes.

The first muffler 19 is provided with a discharge part 28 in a sealed case. The second muffler 22 is closed and communicates with the communication path 30. The communication path 30 is provided across the auxiliary bearing 21, the cylinder 17, and the main bearing 18, and opens into the first muffler 19.

Therefore, the gas refrigerant compressed in the cylinder chamber D opens the first discharge valve mechanism 26a by applying a high pressure to the first discharge valve mechanism 26a through the discharge notch and the first discharge hole 25a. After the gas refrigerant is discharged into the first muffler 19, the gas refrigerant is guided into the sealed case 10 from a discharge part 28 in the sealed case provided in the first muffler 19, and fills the sealed case 10.

On the other hand, the gas refrigerant compressed in the cylinder chamber D applies a high pressure to the second discharge valve mechanism 26b through the discharge notch and the second discharge hole 25b to open the second discharge valve mechanism 26b. To do. After the gas refrigerant is discharged into the second muffler 22, the gas refrigerant is guided to the communication path 30, and is guided to the first muffler 19 through the auxiliary bearing 21, the cylinder 17, and the main bearing 18.

The high-temperature and high-pressure gas refrigerant discharged from the cylinder chamber D into the first muffler 19 and the high-temperature and high-pressure gas refrigerant discharged from the cylinder chamber D into the second muffler 22 have already passed through the communication path 30. Join.

The joined gas refrigerant is guided into the sealed case 10 from the discharge part 28 in the sealed case provided in the first muffler 19 and circulates through the refrigeration cycle components as described above.

FIG. 3 is a plan view of the main bearing 18. FIG. 4 is a plan view of the first cylinder 17A in the two-cylinder type compressor 1. FIG. Note that the cylinder 17 in the one-cylinder type compressor 1A has the same shape, and a description thereof will be omitted below.

As shown in the figure, the communication path 30 for guiding the high-temperature and high-pressure gas refrigerant discharged from the auxiliary bearing 21 into the second muffler 22 into the first muffler 19 is composed of two holes here. The number of holes is not limited. The total cross-sectional area of these communication passages 30 is S1 [mm ² ]. The total cross-sectional area is the total cross-sectional area.

Further, in the first muffler 19 attached to the main bearing 18 shown in FIG. 1 and FIG. 2, the discharge case 28 in the sealed case provided for discharging the high-temperature and high-pressure gas refrigerant stored inside into the sealed case 10. The area is S2 [mm ² ].

Here, from the total cross-sectional area S1 of the communication passage 30, the area S2 of the discharge part 28 in the sealed case 28 provided in the first muffler 19 is set large, that is, S1 <S2.

Therefore, the amount of the high-temperature and high-pressure gas refrigerant released from the discharge part 28 in the sealed case 10 provided in the first muffler 19 into the sealed case 10 is changed from the second muffler 22 through the communication path 30 to the first muffler 19. The amount of gas refrigerant led to

The discharge part 28 in the sealed case can be discharged into the sealed case 10 without increasing the passage resistance of the gas refrigerant, avoiding an overcompressed state in the cylinder chamber 17 and improving efficiency. This is particularly effective when a compact compressor is rotated at a high speed and exhibits high performance.

Further, as shown in FIG. 1 and FIG. 2, in both the 2-cylinder type and 1-cylinder type compressors 1 and 1A, the axial length H of the stator core 16a of the stator 16 in the motor unit 11 is determined. The dimension from the upper end surface, which is one end surface of the stator core 16a, to the one end surface of the sealed case 10, and the member for fixing the compression mechanism 12 to the sealed case 10 from the lower end surface, which is the other end surface of the stator core 16a. That is, when the distance to the end surface of the first cylinder 17A for the 2-cylinder type and the cylinder 17 for the 1-cylinder type is B, the following equation (1) is set to be satisfied.
0.5 <B / A <1 (1)
Hereinafter, the expression (1) is applied to the two-cylinder type compressor 1, but the same conditions apply to the one-cylinder type compressor 1 </ b> A that is not described.
That is, by setting the area S2 of the discharge part 28 in the sealed case 28 provided in the first muffler 19 as described above to be larger than the total cross-sectional area S1 of the communication passage 30, that is, S1 <S2. As a result, the passage resistance can be reduced and the efficiency can be improved. However, on the other hand, the noise reduction effect of the gas refrigerant in the first muffler 19 is reduced, and there is a concern about noise deterioration.

Therefore, the lower space where the distance B from the first cylinder 17A to the lower end surface of the stator core 16a is increased and the high-temperature and high-pressure gas refrigerant is discharged from the discharge part 28 in the sealed case provided in the first muffler 19. Increase the volume. The sealed case 10 is substantially cylindrical, and the space defined by the inner surface of the sealed case 10 is also substantially cylindrical. And the space prescribed | regulated by the part of the range from the 1st cylinder 17A to the stator core 16a in the inner surface of the airtight case 10 is cylindrical.

This makes it possible to reduce the pulsation of the gas refrigerant discharged from the discharge part 28 in the sealed case in the first muffler 19 and suppress noise deterioration.

However, simply increasing the distance B from the first cylinder 17A to the stator core 16a to increase the lower space volume further increases the distance from the first cylinder 17A to the stator 16 and the rotor 15. Will be bigger. Touching of the rotor 15 during operation increases, leading to increased noise and vibration.

Therefore, B / A <1, which can suppress the deterioration of noise, was adopted as the upper limit condition.

The condition of B / A (0.5 <B / A <1) is obtained from [Table 1] below and FIG.

The unit of the noise value is db (decibel). First, from [Table 1], No. 1 will be described. In the conventional example of S1, S1 is larger than S2, that is, opposite to the present embodiment, and B / A is 0.4.
On the other hand, No. in [Table 1]. 2 to No. In this embodiment of FIG. 5, as described above, S2 is made larger than S1, and only B / A is changed by 0.1 in the range of 0.6 to 0.9.

Further, when the area of the first discharge hole 25a provided in the main bearing 18 is S3 [mm ² ], the area S2 [mm ² ] of the discharge part 28 in the sealed case provided in the first muffler 19 is The total cross-sectional area S1 [mm ² ] of the passage 30 and the area S3 [mm ² ] of the first discharge hole 25a are not exceeded. That is, S2 <S1 + S3 is set.

From Table 1, the difference in noise value between the conventional example and the present embodiment was 1 db (decibel) or less, and almost the same result was obtained. Therefore, No. of [Table 1]. 2 to No. This embodiment of 5 can reduce the passage resistance without increasing the noise, and can perform highly efficient compression.

On the other hand, No. in [Table 1]. 6-No. Ten comparative examples are obtained by changing only B / A with respect to those of the present embodiment. As a result, No. B / A is smaller than that of the present embodiment. 6 of 0.4 and No. 6 No. 7 of 0.5 and No. larger than this embodiment. 8 of 1.0 and No. 8 No. 9 of 1.2 has a noise level of no. No. 1 prior art and No. 1 2 to No. 5 is larger than that of the present embodiment.

In addition, No. in [Table 1]. The comparative example of 10 is S1 <S2, and B / A is No.10. The noise measurement value is 0.6 when S2> S1 + S3. As a result, no. The comparative example of No. 10 No. 1 prior art and No. 1 2 is larger than that of the present embodiment.

This is because if the area S2 of the discharge part in the sealed case provided in the first muffler is too large, the effect of reducing the passage resistance is increased, but the effect of reducing the noise in the first muffler is hardly obtained and fixed. This is thought to be because noise cannot be reduced only by the lower space volume below the core.

Moreover, in FIG. 5, the result of the noise test in several examples of this embodiment and a comparative example is shown.
The condition is a two-cylinder type hermetic rotary compressor, and the refrigerant used in the refrigeration cycle is R410A. The total displacement volume of each cylinder is 17.5 cm ³ / rev, which is a relatively small compressor.

The operating rotational speed is 90 rpm, and the pressure conditions are a discharge pressure of 3.2 MPa and a suction pressure of 0.9 MPa. The total cross-sectional area S1 of the communication path 30 described above is 85 mm ² , and the area S2 of the discharge part 28 in the sealed case provided in the first muffler 19 is 100 mm ² . The inner diameter of the sealed case 10 is 110 mm.

In the figure, the black bar graph has B / A of 0.4, which corresponds to the comparative example described above. The white bar graph has a B / A of 0.6 and corresponds to this embodiment. The hatched bar graph has B / A of 1 and 2, and corresponds to the comparative example described above.
As a result, when B / A is set to 0.4 indicated by a black bar graph and the value of the space volume from the cylinder 17A to the lower end surface of the stator core 16a is reduced, the white area is particularly clear at a high frequency of 4 KHz or higher. Noise is larger than in the present embodiment shown in the bar graph.

This is because the value of the space volume B is small, so that the noise in this space is reduced with respect to the noise caused by the gas refrigerant discharged into the sealed case 10 through the sealed case discharge portion 28 provided in the first muffler 19. This is probably because the effect is small.

Further, when B / A is set to 1.2 shown in the hatching bar graph and the value of the spatial volume B from the first cylinder 17A to the stator 16 is increased more than necessary, low frequency noise of 500 Hz or less is obtained. It becomes larger than this embodiment.

This is because the rotor 15 is positioned more together with the stator 16 by increasing the space volume B from the first cylinder 17A to the end face of the stator core 16a. Therefore, it is considered that the swing of the rotor 15 when driving the motor unit 11 is increased, and the compressor noise is increased.

From the above results, when S2 is made larger than S1, that is, S1 <S2, and satisfying the condition of 0.5 <B / A <1 that is the expression (1), the first By enlarging the flow path area of the discharge part in the sealed case provided in the muffler, the passage resistance can be reduced, and an efficient hermetic rotary compressor can be provided while suppressing the deterioration of noise.

In setting the dimension B, the first cylinder 17A is applied as a member for fixing the compression mechanism portion 12 to the sealed case 10, and the distance from the upper end surface to the lower end surface of the stator 16 is set, but the present invention is not limited to this. .
For example, there is a compressor in which the flange portion of the main bearing is enlarged and fixed to the inner peripheral wall of the sealed case. At this time, the first cylinder is formed to have a required minimum diameter and is much smaller than the inner peripheral wall of the sealed case. That is, in such a compressor, a “main bearing” is applied as a member for fixing the compression mechanism portion to the sealed case.

In addition, the following conditions must be satisfied:
When the displacement volume of each of the first and second cylinder chambers D1 and D2 in the 2-cylinder type compressor 1 is V2 [mm ³ ] in the 1-cylinder compressor 1A, the displacement volume of the cylinder chamber D is V2 [mm ³ ]. The relationship with the area S2 [mm ² ] of the discharge part 28 in the sealed case provided in the first muffler 19 is set so as to satisfy the following expression (2).
V2 [mm ³ ] / S2 [mm ² ] <100 [mm] (2)
As shown in FIG. 6, when V2 [mm ³ ] / S2 [mm ² ] is taken on the horizontal axis and the pressure loss is taken on the vertical axis, the change in V2 [mm ³ ] / S2 [mm ² ] is 100. It was found that pressure loss suddenly increased immediately before [mm]. Therefore, V2 [mm ³ ] / S2 [mm ² ] is set so as not to exceed 100 [mm]. That is, V2 [mm ³ ] / S2 [mm ² ] <100 [mm] is set.

FIG. 7A is a plan view of the first cylinder 17A used in the two-cylinder type compressor 1 according to the second embodiment. FIG. 7B is a longitudinal sectional view taken along the line A1-O-A2 of FIG. FIG. 8 is a partial perspective view of the first cylinder 17A. Since the structure other than the cylinder 17A is the same as that of the first embodiment, the same reference numerals as those of the first embodiment are used and description thereof is omitted. In particular, only the 2-cylinder type compressor 1 is set as follows.
A discharge notch 29 is provided in the first cylinder chamber D1 of the first cylinder 17A. The same applies to the second cylinder chamber D2, but the description is omitted. That is, the blade groove 31 is provided in the first cylinder 17A in which the radius of the first cylinder chamber D1 is R1.

A suction hole 32 to which one refrigerant pipe Pa extending from the accumulator 5 is connected is provided on one side of the blade groove 31. A discharge notch 29 is provided at a position opposite to the suction hole 32 via the blade groove 31 and at a predetermined angle θ1 from the center axis with respect to the blade groove 31.

The discharge notch 29 is provided at a depth dimension h, that is, a height dimension h from the end face of the first cylinder in a state inclined by an angle α with respect to the end face of the first cylinder 17A. Although not shown here, the first discharge hole is provided in a portion of the main bearing that faces the discharge notch 29, and the first discharge valve mechanism opens and closes the first discharge hole as described above. It is as follows.

The depth dimension h from the one end face of the first cylinder 17A in the discharge notch 29, that is, the height dimension h, satisfies the following expression (3) with respect to the total height H of the first cylinder 17A. Set to.
H / 2 ≦ h ≦ H (3)
That is, the gas refrigerant compressed in the first cylinder chamber D1 passes through the discharge notch 29 provided in a part of the inner peripheral wall of the first cylinder chamber D1 and the first discharge hole 25a provided in the main bearing 18. And is discharged from the first discharge valve mechanism 26 a to the first muffler 19.
In particular, when the gas refrigerant passes through the first discharge hole 25a, an overcompressed state occurs due to the first discharge hole 25a and the nearby passage resistance, but the discharge notch provided in the first cylinder chamber D1. The amount of overcompression varies greatly depending on the shape and size of 29.

Conventionally, the depth dimension h of the discharge notch is formed to be smaller than the total height H of the first cylinder, that is, half of the thickness dimension H, that is, it is formed to be h <H / 2. In the first cylinder chamber, the gas on the opposite side of the discharge notch across the blade groove 31 does not flow smoothly to the discharge notch. For this reason, the gas refrigerant in the first cylinder chamber is compressed more than necessary and is in an overcompressed state.

Therefore, in the present embodiment, the depth dimension h, that is, the height dimension h of the discharge notch 29 is expressed by the following expression (3) with respect to the total height H of the first cylinder 17A: H / 2 ≦ h ≦ H As a result, the gas refrigerant compressed in the first cylinder chamber D1, particularly the gas refrigerant on the opposite side to the discharge notch across the blade groove 31 in the first cylinder chamber, is notched for discharge. It becomes easy to flow smoothly to 29, and the amount of overcompression during high-speed rotation can be greatly reduced.

FIG. 9 is a longitudinal sectional view of the first cylinder 17A used in the two-cylinder type compressor 1 according to the third embodiment. FIG. 10 is a partial perspective view of the first cylinder 17A. Since the structure other than the first cylinder 17A is the same as that of the first embodiment, the description thereof is omitted.

In particular, only the 2-cylinder type compressor 1 is set as follows.
The discharge notch 29A provided at the same position in the first cylinder chamber D1 is inclined from the end surface of the first cylinder 17A by the angle α to the depth dimension h1 while being inclined with respect to the end surface of the first cylinder 17A. Furthermore, it is provided from the end surface of the first cylinder 17A to the depth dimension h2 in a state inclined by an angle β with respect to the end surface of the first cylinder 17A. The same applies to the second cylinder chamber D2, but the description is omitted.

Thus, it goes without saying that the discharge notches 29A are formed in multiple stages and the entire depth dimension h2 is in a relationship of H / 2 ≦ h2 ≦ H so as to satisfy the expression (3).

In the first cylinder chamber D1, the gas refrigerant in the discharge notch 29A is not compressed even in the compression step, and becomes a so-called dead volume. Again, the gas refrigerant remaining in the discharge notch 29A is re-expanded in a state where the gas refrigerant is sucked into the first cylinder chamber D1 through the suction hole 32, and the corresponding amount of gas refrigerant is restricted from being sucked and lost. Become.

The discharge notch 29A is provided in the main bearing 18 while keeping the dead volume of the discharge notch 29A small by forming the discharge notch 29A in a multi-stage relationship with the relationship of H / 2 ≦ h2 ≦ H in the formula (3). The gas refrigerant can be smoothly guided to the first discharge holes 25a. Therefore, re-expansion loss is suppressed and the amount of overcompression is greatly reduced.

Next, a first muffler according to the fourth embodiment will be described with reference to FIG. In this embodiment, configurations having the same functions as those of the first embodiment are denoted by the same reference numerals as those of the first embodiment, and description thereof is omitted. In the present embodiment, the shape of the discharge part 28 in the sealed case is different from that of the first embodiment. Other structures are the same as those in the first embodiment.

FIG. 12 is a plan view showing the first muffler 19 of the present embodiment. As shown in FIG. 12, in the present embodiment, a plurality of in-sealed case discharge sections 28 are provided, and four are provided as an example. Moreover, the shape of the discharge part 28 in each sealed case is a circle, as in the first embodiment. The total area of the discharge part 28 in the sealed case is the sum of the areas of the discharge parts 28 in the plurality of sealed cases. In the present embodiment, the same effect as in the first embodiment can be obtained. Note that the first muffler 19 of the present embodiment may be used in the second and third embodiments.

Next, a first muffler according to the fifth embodiment will be described with reference to FIG. In this embodiment, configurations having the same functions as those of the first embodiment are denoted by the same reference numerals as those of the first embodiment, and description thereof is omitted. In the present embodiment, the discharge part 28 in the sealed case is different from the first embodiment. Other structures are the same as those in the first embodiment.

FIG. 13 is a plan view showing the first muffler 19 of the present embodiment. As shown in FIG. 13, in this embodiment, the gap formed between the main bearing 18 and the first muffler 19 functions as the sealed case discharge part 28 in the sealed case discharge part 28. This point will be specifically described.

In the present embodiment, the inner diameter of the first muffler 19 is larger than the outer diameter of the main bearing 18. For this reason, when the main bearing 18 is inserted into the first muffler 19, a gap is provided between the first muffler 19 and the main bearing 18. This gap functions as the discharge part 28 in the sealed case. In the present embodiment, the gap provided between the first muffler 19 and the main bearing 18 is connected in a circle. That is, in this embodiment, the discharge part 28 in the sealed case has a shape that is connected in a circular manner. In the present embodiment, the same effect as in the first embodiment can be obtained. Note that the first muffler 19 of the present embodiment may be used in the second and third embodiments.

Further, as described above, one or a plurality of the discharge parts 28 in the sealed case are provided in a part away from the main bearing 18 as in the first and fourth embodiments, and as in the fifth embodiment. A gap between the first muffler 19 and the main bearing 18 may be combined.

As mentioned above, although this embodiment was described, the above-mentioned embodiment is shown as an example and does not intend limiting the range of embodiment. The novel embodiment can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

DESCRIPTION OF SYMBOLS 10 ... Sealed case, 12 ... Compression mechanism part, 13 ... Rotating shaft, 11 ... Electric motor part, 1 ... Sealed rotary compressor (2 cylinder type), 18 ... Main bearing, 22 ... Sub bearing, D1 ... 1st Cylinder chamber, D2 ... second cylinder chamber, 17A ... first cylinder, 17B ... second cylinder, D ... cylinder chamber, 26a ... first discharge valve mechanism, 26b ... second discharge valve mechanism, 19 ... 1st muffler, 22 ... 2nd muffler, 30 ... Communication path, 16 ... Stator, 15 ... Rotor, 25a ... 1st discharge hole, 29 ... Notch for discharge, 1A ... Hermetic rotary compressor (1 cylinder type), 2 ... condenser, 3 ... expansion device, 4 ... evaporator, P ... refrigerant pipe.

Claims

A hermetic rotary compressor in which a compression mechanism portion is housed in a lower portion in a sealed case and an electric motor portion is housed in an upper portion, and the electric motor portion is connected to the compression mechanism portion via a rotating shaft;
The compression mechanism is
One cylinder or two cylinders formed with an inner diameter portion as a cylinder chamber;
A first discharge valve mechanism and a second discharge valve provided on each of the main bearing and the sub-bearing for supporting the rotating shaft, and for discharging and guiding the gas refrigerant compressed in the cylinder chamber; A valve mechanism;
A first muffler that covers the first discharge valve mechanism, temporarily receives the gas refrigerant compressed in the cylinder chamber and silences it, and then discharges it into the sealed case through the discharge part in the sealed case; ,
A second muffler that covers the second discharge valve mechanism and temporarily receives and silences the gas refrigerant compressed in the cylinder chamber;
A communication path provided from the auxiliary bearing to the main bearing, for guiding the gas refrigerant in the second muffler and merging with the gas refrigerant in the first muffler,
When the total cross-sectional area of the communication path is S1 [mm 2 ] and the total area of the discharge part in the sealed case provided in the first muffler is S2 [mm 2 ], S2 is larger than S1 (S1 <S2 )age,
The motor section includes a stator that is inserted into the sealed case, and a rotor that is fitted to the rotating shaft and has an outer peripheral wall provided with a narrow gap from the stator inner peripheral wall. ,
A dimension from the upper end surface of the stator core of the stator to one end surface of the sealing case is A, and a distance from the lower end surface of the stator core to the end surface of the member that fixes the compression mechanism portion to the sealing case is B. When
A hermetic rotary compressor characterized by being set to satisfy the following equation (1).
0.5 <B / A <1 (1)
When the area of the first discharge hole provided in the main bearing and opened and closed by the first discharge valve mechanism is S3 [mm 2 ],
The total area S2 of the discharge part in the sealed case of the first muffler is:
The sum total of the total cross-sectional area S1 of the communication path and the area S3 of the first discharge hole provided in the main bearing does not exceed (S2 <S1 + S3).
The hermetic rotary compressor according to claim 1.
When the excluded volume of one cylinder chamber is V2 [mm 3 ], the relationship with the total area S2 [mm 2 ] of the discharge part in the sealed case of the first muffler satisfies the following equation (2): 2. The hermetic rotary compressor according to claim 1, wherein the hermetic rotary compressor is set as described above.
V2 [mm 3 ] / S2 [mm 2 ] <100 [mm] (2)
When the excluded volume of one cylinder chamber is V2 [mm 3 ], the relationship with the total area S2 [mm 2 ] of the discharge part in the sealed case of the first muffler satisfies the following equation (2): The hermetic rotary compressor according to claim 2, wherein the hermetic rotary compressor is set to be.
V2 [mm 3 ] / S2 [mm 2 ] <100 [mm] (2)
The compression mechanism section includes two cylinders,
A discharge notch is provided in a part of the peripheral wall of the cylinder chamber so as to communicate with the first discharge hole of the main bearing and the second discharge hole of the sub bearing, respectively.
The depth (height) dimension h of the discharge notch from the one end surface of the cylinder is set so as to satisfy the following expression (3) with respect to the total height (thickness dimension) H of the cylinder. The hermetic rotary compressor according to claim 1.
H / 2 ≦ h ≦ H (3)
The compression mechanism section includes two cylinders,
A discharge notch is provided in a part of the peripheral wall of the cylinder chamber so as to communicate with the first discharge hole of the main bearing and the second discharge hole of the sub bearing, respectively.
The depth (height) dimension h of the discharge notch from the one end surface of the cylinder is set so as to satisfy the following expression (3) with respect to the total height (thickness dimension) H of the cylinder. The hermetic rotary compressor according to claim 2.
H / 2 ≦ h ≦ H (3)
The compression mechanism section includes two cylinders,
A discharge notch is provided in a part of the peripheral wall of the cylinder chamber so as to communicate with the first discharge hole of the main bearing and the second discharge hole of the sub bearing, respectively.
The depth (height) dimension h of the discharge notch from the one end surface of the cylinder is set so as to satisfy the following expression (3) with respect to the total height (thickness dimension) H of the cylinder. The hermetic rotary compressor according to claim 3.
H / 2 ≦ h ≦ H (3)
The compression mechanism section includes two cylinders,
A discharge notch is provided in a part of the peripheral wall of the cylinder chamber so as to communicate with the first discharge hole of the main bearing and the second discharge hole of the sub bearing, respectively.
The depth (height) dimension h of the discharge notch from the one end surface of the cylinder is set so as to satisfy the following expression (3) with respect to the total height (thickness dimension) H of the cylinder. The hermetic rotary compressor according to claim 4.
H / 2 ≦ h ≦ H (3)
The hermetic rotary compressor according to any one of claims 1 to 8, the condenser, the expansion device, and the evaporator are connected via a refrigerant pipe to constitute a refrigeration cycle. A refrigeration cycle apparatus characterized by that.