KR200436093Y1 - Rotary two stage compressor and air conditioner using the compressor - Google Patents

Abstract

An object of the present invention is to improve compressor efficiency by optimizing compressor component dimensions such as ratio (V2 / V1) of the amount of pressure in a rotary two-stage compressor for an air conditioner that also uses a refrigerant R410A.

When the ratio (V2 / V1) of the amount of pressure on the high pressure side and the low pressure side is 0.65 to 0.85, the ratio of the cylinder thickness (H2 / H1) is 0.6 to 1.0, the inner radius of the cylinder is Rs, and the outer radius of the roller is Rr. The cylinder shape on the high pressure side was 0.8? Ratio (Rr 2 / Rs 2)? 0.9 and 0.55? Ratio (H 2 / Rs 2)? 0.95.

Compressor, rotary shaft, gas-liquid separator, vane, cylinder, roller

Description

Rotary two stage compressor and air conditioner using the compressor {TWO-STAGE ROTARY COMPRESSOR AND AIR CONDITIONING EQUIPMENT USING THE SAME}

1 is a longitudinal sectional view of a rotary two stage compressor according to the present embodiment;

Fig. 2 is a diagram showing the relationship between the ratio V2 / V1 of the rotary two-stage compressor according to the present embodiment and the cooling and heating average C0P.

3 is a configuration diagram of a two-stage compression injection cycle according to the present embodiment.

Fig. 4 is a diagram showing the relationship between the ratio (H2 / H1) and compressor efficiency of the rotary two stage compressor according to the present embodiment.

Fig. 5 is a diagram showing a load applied to the rotating shaft 2 of the rotary two stage compressor according to the present embodiment.

Fig. 6 is a diagram showing the relationship between the ratio H2 / Rr2 and compressor efficiency of the rotary two-stage compressor according to the present embodiment.

7 is a longitudinal sectional view of a conventional rotary two stage compressor.

8 is a plan view of a compression element of a conventional rotary compressor.

<Explanation of symbols for the main parts of the drawings>

1: compressor

2: axis of rotation

3: gas-liquid separator

4: piping

5: eccentric

6: vane

7: rotor

8: stator

9: main bearing

10: cylinder

11: roller

12: cover part

13: airtight container

14 electric motor

15: middle partition plate

16: spring

17: discharge hole

18: condenser

19: vice bearing

20: compression element

21: bottom part

22: main body

23: evaporator

24: expansion mechanism

25: suction pipe

26, 27: discharge pipe

28: injection euro

29: reputation

30: middle euro

The present invention relates to the high efficiency of a refrigeration cycle, in particular a rotary two stage compressor using an air conditioner with refrigerant R410A as the working fluid.

As a conventional rotary two-stage compressor, a structure disclosed in Japanese Patent Laid-Open No. 60-128990 (Patent Document 1) is known. 7 and 8 show a rotary two stage compressor disclosed in Patent Document 1. FIG.

The compressor 101 shown in FIG. 7 has a closed container 13 composed of a bottom portion 21, a lid portion 12, and a main body portion 22 provided therebetween. The upper part in the airtight container 13 is equipped with the electric motor 14 which consists of the rotor 7 and the stator 8, and the rotating shaft 2 connected to the rotor 7 has two eccentric parts 5a and 5b. The main bearing 9 and the sub bearing 19 are journaled.

The main bearing 9 is fixed to the main body portion 22 of the airtight container 13. There are two compression elements 20, the high pressure side and the low pressure side, which are driven by the eccentric movement of the eccentric portions 5a, 5b of the rotary shaft 2. These compression elements 20 are sandwiched with the high pressure side compression element 20b and the low pressure side compression element 20a in turn from the rotor 7 side by sandwiching the intermediate partition plate 15, and fastening elements such as bolts (not shown). It is fixed and integrated between the main bearing 9 and the sub-bearing 19).

Each compression element 20 mainly comprises a cylinder 10 (low pressure side cylinder 10a, high pressure side cylinder 10b) having a substantially cylindrical portion, and a cylinder 10 provided in the main bearing 9 or the sub bearing 19. ) And a substantially cylindrical roller 11 (low pressure side roller 11a, high pressure side roller 11b) fitted to the outer circumference of the eccentric portion 5, and the spring shown in FIG. Connected to (16) is composed of vanes (16). In each compression element 20, the eccentric part 5 drives the roller 11, rotating eccentrically.

As shown in Fig. 7, the eccentric portion 5a and the eccentric portion 5b of the rotation shaft 2 are 180 degrees out of phase. The phase difference of the compression stroke of each compression element 20 is also 180 degrees.

The flow of the refrigerant which is the working fluid is shown by the arrow in FIG. The refrigerant is first drawn in through the intake pipe 25a at the low pressure Ps, and then compressed to the intermediate pressure Pm at the low pressure side compression element 20a. The refrigerant compressed to the intermediate pressure Pm is discharged out of the low pressure side compression element 20a from the discharge hole 17 (see Fig. 8). Here, the pressure ratio (discharge pressure / intake pressure) of the low pressure side compression element 20a is (Pm / Ps). Incidentally, Fig. 8 is a view of each compression element 20 viewed from the axial direction of the rotating shaft 2, and is used for common description of the low pressure side compression element 20a and the high pressure side compression element 20b.

The discharged refrigerant of the intermediate pressure Pm is once made into the high pressure space and the shielded intermediate space 30 in the sealed container 13 which is formed of the concave portion of the sub-bearing 19 and the flat plate 18 provided on the side opposite to the end plate surface. Downflow. The refrigerant discharged out of the sealed container 13 from the intermediate space 30 through the discharge pipe 26a is taken in by the high pressure side compression element 20b through the intake pipe 25b.

The refrigerant compressed up to the high pressure Pd by the high pressure side compression element 20b is discharged into the sealed container 13 through the discharge hole 17 (see Fig. 8). The refrigerant discharged into the sealed container 13 is discharged out of the compressor 101 through the discharge pipe 26b with the refrigerant pressure in the sealed container 13 being the high pressure Pd. The pressure ratio of the high pressure side compression element 20b is here (Pd / Pm).

As described above, according to the two-stage compressor 101 which sequentially compresses the two compression elements 20, the pressure ratio Pm / Ps or Pd / Pm of each compression element 20 is compressed in one step. It becomes smaller than the pressure ratio Pd / Ps of a single stage compressor. Therefore, it can be seen that the re-expansion loss of the refrigerant and the leakage loss of the refrigerant depending on the pressure ratio can be reduced, thereby improving the compressor efficiency (= compressor input used to compress the refrigerant).

On the other hand, Japanese Patent Laid-Open No. 60-259790 (Patent Document 2) is disclosed as optimizing a part dimension of a compressor. Although patent document 2 is a single stage rotary compressor, the technique which improves compressor efficiency by optimizing the component dimensions of a compressor is disclosed. When the thickness of the cylinder 10 shown in FIGS. 7 and 8 is H, the inner circumferential radius of the cylinder 10 is Rs, and the outer circumferential radius of the roller 11 is Rr, the ratio (Rr / Rs) is 0.84 to 0.92. When the ratio (H / Rs) is 0.4 to 0.8, it is disclosed that the mechanical friction loss is reduced and the compressor efficiency is improved.

[Patent Document 1] Japanese Patent Laid-Open No. 60-128990 (No. 5 page, Fig. 1)

[Patent Document 2] Japanese Patent Application Laid-Open No. 60-259790 (No. 6 page, Fig. 8)

The conventional rotary two-stage compressor disclosed in Patent Document 1 is a case where a difference between the evaporation temperature and the condensation temperature, such as a heat pump hot water heater, is used in a refrigeration cycle having a large pressure ratio (Pd / Ps), and the high pressure side compression element 20b. The ratio (V2 / V1) was set to 0.45 to 0.65 when the amount of pressure in the compression chamber capacity (or cylinder capacity) is V2 and the amount of pressure in the low pressure side compression element 20a is V1.

However, in the rotary two-stage compressor for air conditioner using the refrigerant R410A as the working fluid, the pressure ratio (Pd / Ps) can be made relatively small, and there is a problem that the ratio (V2 / V1) for improving the compressor efficiency is different from the conventional one. In addition, when the rotary two-stage compressor is used in the injection cycle, which is a more efficient cycle, the ratio (V2 /) that improves the cooling / heating average COP (= average cooling capacity / input and rated heating capacity / input) which is composed of the compressor efficiency and the injection cycle efficiency. There is a problem that V1) is different from the conventional one.

In addition, the pressure ratio of each compression element is small in the rotary two-stage compressor, unlike the single-stage rotary compressor with respect to the component dimensions of the compressor. Therefore, it is considered that the loss ratio of mechanical friction loss and refrigerant leakage loss compared to the single stage compressor is different. In addition, in the rotary two-stage compressor, two compression elements of different shapes are driven by the same rotary shaft 2, so that a load or centrifugal imbalance occurs due to refrigerant compression in each compression element, thereby minimizing mechanical friction loss. / Rs) and the ratio (H / Rs) has a problem that is different from the conventional.

An object of the present invention is to provide a rotary two stage compressor for improving the compressor efficiency in a rotary two stage compressor for an air conditioner having a small pressure ratio using a working fluid having the same properties as the refrigerant R410A.

In addition, another object of the present invention is to provide an air conditioner having an air conditioner equipped with a rotary two-stage compressor to improve the cooling and heating average COP.

In order to achieve the object of the present invention, the rotary two-stage compressor of the present invention includes a motor, a low pressure side compression element driven by the electric motor, and a working fluid driven by the motor and compressed by the low pressure side compression element in a sealed container. A high pressure side compression element for compression was provided, and 0.65 ≦ ratio (V2 / V1) ≦ 0.85 when the amount of pressure on the high pressure side compression element was V2 and the amount of pressure on the low pressure side compression element was V1.

The above configuration can provide a rotary two-stage compressor that achieves excellent compressor efficiency even when applied to a refrigeration cycle or injection cycle for an air conditioner with a small pressure ratio.

In order to achieve the above object, in addition to the configuration of the rotary two-stage compressor described above, the working fluid may be the refrigerant R410A.

Moreover, in order to achieve the said objective, in addition to the structure of the rotary two stage compressor mentioned above, the rotary shaft which rotates by the said electric motor, and the partition plate provided between the said low pressure side compression element and the high pressure side compression element are further provided, The low pressure side compression element and the high pressure side compression element may be connected via the partition plate.

Moreover, in order to achieve the said objective, in addition to the structure of the rotary two stage compressor mentioned above, each said compression element is equipped with the cylinder of a substantially cylindrical shape, and the roller of the substantially cylindrical shape fitted to the eccentric part of the said rotating shaft, When the thickness of the cylinder of the high pressure side compression element is H2 and the cylinder thickness of the low pressure side compression element is H1, 0.6? Ratio (H2 / H1)? 1.0 may be set.

Moreover, in order to achieve the said objective, in addition to the structure of the rotary two stage compressor mentioned above, each said compression element is equipped with the cylinder of a substantially cylindrical shape, and the roller of the substantially cylindrical shape fitted to the eccentric part of the said rotating shaft, When the inner circumferential radius of the cylinder of the high-pressure side compression element is Rs2, and the outer circumferential radius of the roller is Rr2, and when 0.8 ≤ ratio (Rr2 / Rs2) ≤ 0.9, 0.55 ≤ ratio (H2 / Rs2) ≤ 0.95.

In addition, in order to achieve another object of the present invention, the air conditioner of the present invention in the air conditioner having a refrigeration cycle in which the condenser, expansion mechanism, evaporator, compressor in order to connect the piping, the compressor is a motor And a high pressure side compression element driven by the electric motor, and a high pressure side compression element driven by the electric motor to compress the working fluid compressed by the low pressure side compression element, and the amount of pressure suppressed by the high pressure side compression element V2, When the amount of depressurization of the low pressure side compression element was V1, a rotary two-stage compressor having 0.65? Ratio (V2 / V1)? 0.85 was used.

According to the said structure, even if it applies to the refrigeration cycle or injection cycle for air conditioners with a small pressure ratio, it can provide the air conditioner which improves an air-conditioning average COP.

In order to achieve the above another object, in addition to the configuration of the air conditioner described above, the working fluid may be a refrigerant R410A.

In order to achieve the above another object, in addition to the configuration of the air conditioner described above, each of the compression elements includes a substantially cylindrical cylinder and a substantially cylindrical roller fitted to an eccentric portion of the rotating shaft, When the thickness of the cylinder of the compression element is H2 and the cylinder thickness of the low pressure side compression element is H1, 0.6? Ratio (H2 / H1)? 1.0 may be set.

In order to achieve the above another object, in addition to the configuration of the air conditioner described above, each of the compression elements includes a substantially cylindrical cylinder and a substantially cylindrical roller fitted to an eccentric portion of the rotating shaft, When the inner circumferential radius of the cylinder of the compression element is Rs2, and the outer circumferential radius of the roller is Rr2, and 0.8 ≦ ratio (Rr2 / Rs2) ≦ 0.9, 0.55 ≦ ratio (H2 / Rs2) ≦ 0.95.

EMBODIMENT OF THE INVENTION Below, one Embodiment of this invention is described using drawing. 6 and 7, the same reference numerals are used for the same components as in Figs. 1 to 5 to facilitate understanding of the present embodiment.

Fig. 1 shows a side cross section of the compressor 1 of this embodiment. The compressor 1 of this embodiment applies a working fluid to the refrigerating cycle for room air conditioners of refrigerant | coolant R410A. The compressor 1 shown in FIG. 1 has a closed container 13 composed of a bottom portion 21, a lid portion 12, and a main body portion 22 provided therebetween. The upper part in the airtight container 13 is equipped with the electric motor 14 which consists of the rotor 7 and the stator 8, and the rotating shaft 2 connected to the rotor 7 has two eccentric parts 5a and 5b. The main bearing 9 and the sub bearing 19 are journaled.

The main bearing 9 is fixed to the main body portion 22 of the airtight container 13. There are two compression elements 20, the high pressure side and the low pressure side, which are driven by the eccentric movement of the eccentric portions 5a, 5b of the rotary shaft 2. These compression elements 20 are sandwiched with the high pressure side compression element 20b and the low pressure side compression element 20a in turn from the rotor 7 side by sandwiching the intermediate partition plate 15, and fastening elements such as bolts (not shown). It is fixed and integrated between the main bearing 9 and the sub-bearing 19).

Each compression element 20 mainly comprises a cylinder 10 (low pressure side cylinder 10a, high pressure side cylinder 10b) having a substantially cylindrical portion, and a cylinder provided in the main bearing 9 or the sub bearing 19 ( End plate surface in contact with 10), a substantially cylindrical roller 11 (low pressure side roller 11a, high pressure side roller 11b) fitted to the outer circumference of the eccentric portion 5, and a spring (not shown). It is composed of vanes (not shown) connected to. In each compression element 20, the eccentric part 5 drives the roller 11, rotating eccentrically.

The roller 11 eccentrically rotates the cylindrical inner circumference of the cylinder 10 clamped by the end plate surface of the main bearing 9 or the sub bearing 19 and the intermediate partition plate 15. The vane with respect to the roller 11 forms a compression chamber by partitioning the inner peripheral part of the cylinder 10. Specifically, there is a minute gap between the roller 11 and each member, and the gap is prevented by lubricating oil stored in the bottom portion of the airtight container 13 to prevent sliding of the members, thereby preventing the compression chamber 31a. , 31b).

As shown in Fig. 1, the eccentric portion 5a and the eccentric portion 5b of the rotation shaft 2 are 180 degrees out of phase. The phase difference of the compression stroke of each compression element 20 is also 180 degrees.

The flow of the refrigerant which is the working fluid is shown by the arrow in FIG. The refrigerant is first drawn in through the intake pipe 25a at the low pressure Ps, and then compressed to the intermediate pressure Pm at the low pressure side compression element 20a. The refrigerant compressed to the intermediate pressure Pm is discharged out of the low pressure side compression element 20a from a discharge hole (not shown) provided in the compression chamber of the low pressure side compression element 20a. Here, the pressure ratio (discharge pressure / intake pressure) of the low pressure side compression element 20a is (Pm / Ps).

The discharged refrigerant of the intermediate pressure Pm is once made into the high pressure space and the shielded intermediate space 30 in the sealed container 13 which is formed of the concave portion of the sub-bearing 19 and the flat plate 18 provided on the side opposite to the end plate surface. Downflow. The refrigerant discharged out of the sealed container 13 from the intermediate space 30 through the discharge pipe 26a is taken in to the high pressure side compression element 20b through the intake pipe 25b.

The refrigerant compressed to the high pressure Pd by the high pressure side compression element 20b is discharged into the sealed container 13 through discharge holes (not shown) provided in the compression chamber of the high pressure side compression element 20b. The refrigerant discharged into the sealed container 13 is discharged out of the compressor 1 through the discharge pipe 26b with the refrigerant pressure in the sealed container 13 being the high pressure Pd. The pressure ratio of the high pressure side compression element 20b is here (Pd / Pm).

The structure of the compressor 1 is substantially the same as that of the conventional rotary two-stage compressor 101 shown in Figs. 7 and 8, but the compressor component dimensions are different. In this embodiment, the main dimension ratio of the compressor components was as follows. The thicknesses of the cylinders 10a and 10b are H1 and H2, the inner circumferential radii of the cylinders 10a and 10b are Rs1 and Rs2, and the outer circumferential radii (outer diameters) of the rollers 11a and 11b are Rr1 and Rr2. In addition, the dimension ratio when the amount of pressure of the high pressure side compression element 20b is set to V2 and the amount of pressure of the low pressure side compression element 20a is set to V1 is 0.65 ≦ (V2 / V1) ≦ 0.85, 0.6 ≦ ratio (H2 / H1) <1.0, 0.8 <ratio (Rr2 / Rs2) <0.9, 0.55 <ratio (H2 / Rs2) <0.95. The reason will be described below.

The case where the rotary two stage compressor 1 is used for an air conditioner (two stage compression cycle) in which the working fluid is the refrigerant R410A is described. FIG. 2 shows the relationship between the ratio V2 / V1 of the amount of pressure in the compression element 20 on the high pressure side and the low pressure side, and the cooling and heating average C0P improvement rate of the two-stage compression cycle. Here, the cooling and heating average COP improvement rate is the improvement rate of the cooling and heating average COP by two stage compression cycles. Compared to the heating and cooling average COP of a cycle using a conventional single stage compressor.

Fig. 2 shows the application of the rotary two-stage compressor of the present embodiment to a normal cycle as a refrigeration cycle as a two-stage compression cycle, in which a refrigerant gas after heat-exchange is injected into a refrigerant compressed by the low pressure side compression element 20a. The injection cycle is shown as a two stage compressed gas injection cycle. In addition, this two stage compressed gas injection cycle is mentioned later.

As shown in Fig. 2, in the two-stage compression cycle, the cooling and heating average C0P improvement rate becomes maximum when the amount of suppression amount (V2 / V1) is about 0.65. When the pressure reduction ratio V2 / V1 is smaller than 0.65, the compression operation of the low pressure side compression element 20a is performed, and when the pressure reduction ratio V2 / V1 is larger than 0.65, the compression operation of the high pressure side compression element 20b is performed. Relatively large.

Therefore, in the two-stage compression cycle, the cooling and heating average COP is improved in the range of 0.5 ≦ pressurization amount ratio (V2 / V1) ≦ 0.8 where the difference in the cooling and heating average COP improvement ratio which effectively utilizes the two compression elements 20 at the same time is small. In particular, when the R410A refrigerant is used, the amount of pressure in the high pressure side compression element 20b is at least half the amount of pressure in the low pressure side compression element 20a, and the conventional amount of pressure in the patent document 1 (V2 / V1) is 0.45 to 0.65. In contrast, the scope is clearly different.

Next, a case where the rotary two stage compressor 1 is used in the injection cycle shown in FIG. 3 will be described. The refrigeration cycle, which is usually used for air conditioners (air conditioners), has a condenser, expansion mechanism, evaporator, and compressor connected to the pipe, whereas the two-stage compression injection cycle connects the compressor (1) and the pipe (4). A gas-liquid separator 3 for separating the liquid phase and the gaseous phase of the refrigerant downstream of the first expansion mechanism 24a provided downstream of the 18, and a second expansion mechanism provided between the gas-liquid separator 3 and the evaporator 23. 24b, the injection flow path 28 by the intermediate flow path 30 which communicates with the piping which connects the gas-liquid separator 3 and each compression element 20 is provided.

The operation of this two stage compression injection cycle will be described. The refrigerant discharged at the high pressure Pd from the rotary two-stage compressor 1 is first condensed by the condenser 18. The condensed refrigerant is expanded to the intermediate pressure Pm in the first expansion mechanism 24a. The medium pressure Pm refrigerant is separated into the gas phase and the liquid phase in the gas-liquid separator 3, and mainly the gas phase component flows downward into the injection passage 28, and mainly the liquid phase component flows downward into the expansion mechanism 24b. Mainly, the liquid component is expanded in the second expansion mechanism 24b to the low pressure Ps, evaporated in the evaporator 23 and taken into the low pressure side compression element 20a.

The refrigerant compressed to the intermediate pressure Pm at the low pressure side compression element 20a is mixed with the refrigerant flowing down the injection flow path 29 and compressed to the high pressure Pd at the high pressure side compression element 20b. This injection cycle bypasses the gaseous components not contributing to the heat exchange of the evaporator 23 by the injection flow path 28 at an intermediate pressure Pm (> Ps), thereby reducing the power of the low pressure side compression element 20a. It improves cooling and heating average COP.

In this two-stage compression injection cycle, the ratio V2 / V1 of the amount of the forcing to maximize the heating and cooling average C0P improvement rate is about 0.85, which is larger than that of the two-stage compression cycle as shown in FIG. This is an effect of increasing the bypass flow rate (hereinafter, referred to as an injection flow rate) through the injection flow path as the amount of the suppression amount ratio V2 / V1 is increased.

Therefore, in this cycle, heating and cooling of the two-stage compression injection cycle consists of 0.65 ≤ pressure reduction ratio (V2 / V1) ≤ 1.0, in which the heating and cooling average COP improvement rate is not completely reduced, centering around 0.85, which is the maximum of the heating and cooling average COP improvement rate. Average COP is improved.

In addition, the heating / heating average C0P is improved in the range where the amount of suppressed amount ratio V2 / V1 does not fall within the type of cycle, that is, in a range of 0.65 ≦ pressurized amount ratio V2 / V1 ≦ 0.85 including the maximum values of both types. In the rotary two-stage compressor 1 of the present embodiment, the ratio of the ratio of the ratio (V2 / V1) 0.45 to 0.65 of the conventional ratio (V2 / V1) 0.45 to 0.65 in Patent Literature 1 is set to 0.65? In both the compression cycle and the two-stage compression injection cycle, the cooling and heating average C0P can be improved, and the design universality is also improved.

Next, another performance improvement will be described in the embodiment of the present invention. Hereinafter, the ratio (V2 / V1) of the amount of the forcing is set in the range of 0.65 to 0.85. In addition, the inner circumferential radius Rs of the cylinder 11 was set to the same value as the high-pressure side compression element 20b and the low-pressure side compression element 20a from the design versatility and assemblability (the difference between the two dimensions here was ± 1.2%). ).

Fig. 4 shows the relationship between the ratio H2 / H1 of the thickness of the cylinder 11 on the high pressure side and the low pressure side, and the compressor efficiency in the two-stage compression cycle for the air conditioner. From Fig. 4, the cylinder thickness ratio H2 / H1 is about 0.8, and the compressor efficiency is maximized.

The principle that a compressor efficiency has the maximum value with respect to the ratio (H2 / H1) of the thickness of the cylinder 11 of a high pressure side and a low pressure side is demonstrated using FIG. The rotary two-stage compressor 1 shown in Fig. 1 has a rotational centrifugal force Fc of the roller 11 and the eccentric portion 5 on the eccentric portion 5 of the rotary shaft 2, and a compression load Fr from the refrigerant. This works.

Since the rotational centrifugal force Fc increases with the eccentricity e, the eccentricity e increases with the reduction of the thickness H of the cylinder 10, so the rotational centrifugal force Fc increases with the decrease of H. do.

The compressive load Fr increases with the projected area of the load (the outer radius Rr of the roller 11 × 2 × thickness H), and the projected area with the thickness H of the cylinder 10. Is increased. Therefore, the compressive load Fr increases with H.

Therefore, there exists a ratio (H / Rs) that maximizes the compressor efficiency by the combined force of the rotational centrifugal force (Fc) and the compression load (Fr). For example, in the conventional single stage compressor disclosed in Patent Document 2, the ratio 0.82? In (Rr / Rs) ≤ 0.94, 0.4 ≤ ratio (H / Rs) ≤ 0.8.

On the other hand, in the rotary two-stage compressor r1 in the present embodiment, there are ratios H1 / Rs1 and H2 / Rs2 for improving the compression efficiency with each compression element 20. In the present embodiment, the ratio V2 / V1 of the amount of the forcing is 0.65 to 0.85 and the inner circumferential radius Rs1 = Rs2 of the cylinder 10, and the ratio H2 / of the cylinder thickness from (H2 / Rs2) / (H1 / Rs1). The dominant dimension can be summarized by H1).

As a result, the compressor efficiency is improved in the range of 0.65? Cylinder thickness ratio (H2 / H1)? 1.0. Compressor efficiency in the area 0.65 ≤ (H2 / H1) ≤ 1 in the two-stage compression cycle of R410A, ratio of the amount of suppression (V2 / V1) 0.65 ≤ (V2 / V1) ≤ 0.85 This was improved.

Next, Fig. 6 shows the relationship between the thickness H2 of the cylinder 10b on the high pressure side and the compressor efficiency. When the ratio (V2 / V1) is set to 0.65 to 0.85 and the ratio (H1 / H2) is set to 0.65 to 1.0, the ratio (H2 / Rs2) of the thickness H2 of the cylinder 10b on the high pressure side and the inner circumferential radius Rs2 And the relationship with the compressor efficiency. In this case, the amount of indentation (V1) was examined in the range of 9.1 mL / rev to 14 mL / rev, and the ratio (Rr2 / Rs1) was 0.8 to 0.9. 6, the compressor efficiency is improved in the range of 0.55? Ratio (H2 / Rs2)? 0.95.

When the ratio H2 / Rs2 is small, leakage loss between the outer circumferential surface of the roller 11b and the inner circumferential surface of the cylinder 10b is small, while mechanical frictional losses such as vane sliding movement loss are increased. On the contrary, when the ratio H2 / Rs2 is large, the leakage loss is large and the mechanical friction loss is small. In addition, the influences of the aforementioned compression load Fr2 and rotational centrifugal force Fc2 are applied. In the rotary two-stage compressor 1, since the pressure ratio of each compression element 20 is small, the influence of a leakage loss is small compared with a mechanical friction loss. Therefore, the proper ratio (H2 / Rs2) of the rotary two stage compressor 1 is 0.55 to 0.95, and is larger than the value 0.4 to 0.8 of the conventional single stage compressor.

As described above, the rotary two-stage compressor to which the embodiment of the present invention is applied has a ratio (V2 / V1) of the amount of pressure suppressed to 0.65 to 0.85. Therefore, the two-stage compression cycle and the two-stage compression injection cycle for an air conditioner having a small pressure ratio Both heating and cooling average COP is improved. Moreover, since the ratio (H2 / H1) of the thickness of the cylinder was set to 0.65 to 1.0, the compressor efficiency is improved by optimizing the rotation centrifugal force applied to the rotating shaft and the compression load.

In addition, since 0.8 ≤ ratio (Rr2 / Rs1) ≤ 0.9 or 0.55 ≤ ratio (H2 / Rs2) ≤ 0.95 with respect to the high-pressure side compression element 20b, the compressor efficiency was improved by optimizing the ratio of refrigerant leakage loss and mechanical friction loss. Improve.

It is possible to improve the efficiency of the compressor by optimizing the ratio of the pressurization amount (V2 / V1), the compressor components of each compression element, to reduce mechanical friction loss, and to properly purify the ratio of refrigerant leakage loss and mechanical friction loss. .

Rotary two-stage compressor of the present invention can improve the efficiency of the compressor by optimizing the balance of refrigerant leakage loss, mechanical friction loss, load.

In addition, the air conditioner equipped with a rotary two-stage compressor to which the present invention is applied can improve the cooling and heating average C0P.

Claims (10)

A high pressure side compression element for compressing a working fluid compressed into the low pressure side compression element driven by the electric motor and driven by the electric motor in the sealed container, Each said compression element comprises a substantially cylindrical cylinder and a substantially cylindrical roller fitted to an eccentric portion of said rotating shaft, When the pressure of the high pressure side compression element is V2 and the pressure of the low pressure side compression element is V1, 0.65? Ratio (V2 / V1)? 0.85, When the inner circumferential radius of the cylinder of the high pressure side compression element is Rs2, the outer circumference radius of the roller is Rr2, the thickness of the cylinder of the high pressure side compression element is H2, and 0.8 ≦ ratio (Rr2 / Rs2) ≤ 0.9, 0.55 ≤ ratio (H2 / Rs2) ≤ 0.95 Rotary two-stage compressor characterized in that. The rotary two stage compressor of claim 1, wherein the working fluid is refrigerant R410A. The low pressure side compression element and the high pressure side compression element according to claim 1, further comprising a rotary shaft rotating by the electric motor, and a partition plate provided between the low pressure side compression element and the high pressure side compression element. Rotary two stage compressor connected via a partition plate. The rotary two-stage compressor according to claim 1, wherein 0.6 ≦ ratio (H2 / H1) ≦ 1.0 when the thickness of the cylinder of the high pressure side compression element is H2 and the cylinder thickness of the low pressure side compression element is H1. In an air conditioner having a refrigeration cycle in which a condenser, an expansion mechanism, an evaporator, and a compressor are sequentially connected by pipes, the compressor is driven by an electric motor, a low pressure side compression element driven by the electric motor, and driven by the electric motor in a sealed container. A high pressure side compression element for compressing the working fluid compressed by the low pressure side compression element, Each said compression element comprises a substantially cylindrical cylinder and a substantially cylindrical roller fitted to an eccentric portion of said rotating shaft, When the pressure of the high pressure side compression element is V2 and the pressure of the low pressure side compression element is V1, 0.65? Ratio (V2 / V1)? 0.85, The inner circumference radius of the cylinder of the high pressure side compression element is Rs2, the outer circumference radius of the roller is Rr2, the thickness of the cylinder of the high pressure side compression element is H2, When 0.8 ≤ ratio (Rr2 / Rs2) ≤ 0.9, 0.55 ≤ ratio (H2 / Rs2) ≤ 0.95 As one air conditioner. In an air conditioner having a refrigeration cycle in which a condenser, an expansion mechanism, an evaporator, and a compressor are sequentially connected by pipes, The expansion mechanism consists of a first expansion mechanism and a second expansion mechanism, and has a gas-liquid separator connected to those first and second expansion mechanisms, The compressor includes an electric motor in a closed container, a low pressure side compression element driven by the electric motor, and a high pressure side compression element driven by the electric motor to compress a working fluid compressed by the low pressure side compression element, Each said compression element comprises a substantially cylindrical cylinder and a substantially cylindrical roller fitted to an eccentric portion of said rotating shaft, When the pressure of the high pressure side compression element is V2 and the pressure of the low pressure side compression element is V1, 0.65? Ratio (V2 / V1)? 0.85, The inner circumference radius of the cylinder of the high pressure side compression element is Rs2, the outer circumference radius of the roller is Rr2, the thickness of the cylinder of the high pressure side compression element is H2, When 0.8 ≤ ratio (Rr2 / Rs2) ≤ 0.9, 0.55 ≤ ratio (H2 / Rs2) ≤ 0.95 And a gas-liquid separator in communication with a flow passage through the working fluid compressed by the low pressure side compression element. The air conditioner according to claim 5 or 6, wherein the working fluid is refrigerant R410A. The air conditioner according to claim 5 or 6, wherein 0.6? Ratio (H 2 / H 1)? delete delete

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