KR101309464B1 - Compressor - Google Patents

Abstract

[assignment]
Even if the through-hole of the cylinder into which the connecting pipe is press-fitted has the shape of a cross-section, a compressor is provided which can ensure the integrity of the connecting pipe and the through-hole of the cylinder without using an elastic material such as an O-ring or a sealing tape. .
[Solution]
In the compressor 1, the thickness of the 1st cylinder 2a of the part which becomes the outer side of the linear part of the gas suction hole 11a in the state before the coupling pipe 12 is press-fitted into the gas suction hole 11a is A When the long side length in the cross section of the gas suction hole 11a is defined as B, and the short side length in the cross section of the gas suction hole 11a is defined as C, the coupling pipe 12 is defined as the gas suction hole 11a. ), The value of A × B / C is defined so that the deformation that the coupling pipe 12 is convex toward the inner circumference does not occur.

Description

COMPRESSOR

The present invention relates to a compressor.

Conventionally, in the compressor, a cylindrical pipe connecting pipe communicating with the compression chamber is press-fitted to the side surface of the cylinder in which the compression chamber is formed. For example, in the high pressure shell compressor in which the sealed container becomes discharge pressure, the coupling pipe which connects the low pressure side of a refrigerating cycle circuit and a compression chamber is provided. For example, in the low pressure shell type compressor in which the sealed container becomes suction pressure, the coupling pipe which connects the high pressure side of a refrigeration cycle circuit, and a compression chamber is provided. For example, in a multistage compressor that sequentially compresses refrigerant in a plurality of compression chambers, the compression chamber on the low stage side and the compression chamber on the high stage side are connected by a coupling pipe.

By the way, if the thickness of the cylinder can be made thin, the compressor can be miniaturized, and the multi-cylinder can be made without increasing the shell capacity of the compressor. In the rotary compressor, by reducing the thickness of the cylinder, the diameter of the inner circumferential surface of the cylinder and the diameter of the rotary piston can be increased without changing the compression chamber capacity. It is possible to reduce refrigerant leakage. However, in the case where the thickness of the cylinder is made thin in this manner, the diameter of the through-hole (ie, the through-hole communicating with the compression chamber) of the cylindrical connecting pipe or the cylinder into which the connecting pipe is pressurized should be made small depending on the thickness of the cylinder. The flow rate of the refrigerant flowing through the compression chamber is reduced.

Therefore, in the conventional compressor, it is proposed that the shape of the connecting pipe communicating with the compression chamber and the through hole of the cylinder into which the connecting pipe is press-fitted is formed in the shape of a cross section (see Patent Document 1). . By forming the shape of the connecting pipe and the through-hole of the cylinder into which the connecting pipe is press-fitted in the shape of a cross section, the compression chamber can be secured because the cross section of the flow path of the connecting pipe and the through-hole of the cylinder into which the connecting pipe is press-fitted can be secured. The thickness of a cylinder can be made thin, preventing the fall of the flow volume of the refrigerant | coolant which flows.

Japanese Patent Application Laid-Open No. 2010-121481

However, when the through-hole of the cylinder into which the connecting pipe is press-fitted has a cross-sectional elliptical shape, when the coupling pipe is pressed into the through-hole of the cylinder, there is a possibility that the flat portion of the coupling pipe deforms to the inner circumferential side of the coupling pipe. For this reason, the seal | sticker property of a connection pipe and the through-hole of the cylinder which this connection pipe press-fits may deteriorate. Therefore, there exists a problem that the gas leakage loss at the time of compression increases, and the performance of a compressor falls.

Here, conventionally, in order to secure a seal | sticker, although there exists a method of sealing using elastic materials, such as an O-ring and a seal tape, it is unpreferable considering workability and cost. Moreover, in the case of a compressor, when connecting a coupling pipe and piping of the low pressure side of a refrigeration cycle circuit, it is connected by welding. For this reason, in the case of a compressor, when the method of sealing using elastic materials, such as an O-ring and a seal tape, is used, the problem will arise that an elastic material will deteriorate by the heat at the time of welding, and the reliability of a compressor will fall.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-described problems. Even if the through-hole of the cylinder into which the connecting pipe is press-fitted has a cross-sectional oblong shape, the connecting pipe and the sealing pipe are not used. It is an object of the present invention to provide a compressor that can ensure the practicality of the cylinder through-hole.

The compressor which concerns on this invention is equipped with the cylinder in which the compression chamber was formed inside, and the coupling pipe which is attached to the cylinder and communicates with the said compression chamber, The cylinder penetrates the said compression chamber from the side surface of the cylinder, and has a long side. The cross-sectional oblong through-hole formed so that a direction may follow the circumferential direction of the cylinder is formed, At least one edge part is formed in cross-sectional oblong shape, The one end part is the said through-hole. The cylinder of the part which is press-fitted to 0.05 mm or less and communicates with the compression chamber, and which is outside of the straight portion of the through-hole before the coupling pipe is press-fitted into the through-hole. When the thickness is defined as A, the long side length in the cross section of the through hole is B, and the short side length in the cross section of the through hole is defined as C, the coupling When the thickness t of the pipe is 0 mm <t ≦ 1.6 mm, 0 <A × B / C ≦ 3.38, and when the thickness t of the coupling pipe is 0 mm <t ≦ 1 mm, 0 < When AxB / C≤2.88 and the thickness t of the coupling pipe is 0mm <t≤0.4mm, 0 <AxB / C≤2.38.

Moreover, the compressor which concerns on this invention is equipped with the cylinder in which the compression chamber was formed inside, and the coupling pipe which is attached to the cylinder and communicates with the said compression chamber, The said cylinder penetrates into the said compression chamber from the side surface of the cylinder, And a cross-sectional oblong through-hole formed so that the long side direction is along the circumferential direction of the cylinder, wherein at least one end thereof is formed into a cross-sectional oblong, and one end thereof is press-fitted into the through-hole. The cylinder is pressurized to about 0.1 mm or less and communicates with the compression chamber, and the thickness of the cylinder of the portion which becomes the outside of the straight portion of the through hole in the state before the coupling pipe is pressed into the through hole is A and the through hole. When the long side length in the cross section of B is defined and the short side length in the cross section of the through hole is defined as C, the coupling pipe When the thickness t is 0 mm <t ≦ 1.6 mm, 0 <A × B / C ≦ 3.28, and when the thickness t of the coupling pipe is 0 mm <t ≦ 1 mm, 0 <A × When B / C≤2.83 and the thickness t of the coupling pipe is 0mm <t≤0.4mm, 0 <A x B / C≤2.37.

Moreover, the compressor which concerns on this invention is equipped with the cylinder in which the compression chamber was formed inside, and the coupling pipe which is attached to the cylinder and communicates with the said compression chamber, The said cylinder penetrates into the said compression chamber from the side surface of the cylinder, And a cross-sectional oblong through-hole formed so that the long side direction is along the circumferential direction of the cylinder, wherein at least one end thereof is formed into a cross-sectional oblong, and one end thereof is press-fitted into the through-hole. The cylinder is pressurized to 0.15 mm or less and communicates with the compression chamber, and the thickness of the cylinder of the portion of the straight portion of the through hole in the state before the coupling pipe is pressed into the through hole is A and the through hole. When the long side length in the cross section of B is defined and the short side length in the cross section of the through hole is defined as C, the coupling pipe When the thickness t is 0 mm <t ≦ 1.6 mm, 0 <A × B / C ≦ 3.2, and when the thickness t of the coupling pipe is 0 mm <t ≦ 1 mm, 0 <A × When B / C ≦ 2.8 and the thickness t of the coupling pipe is 0 mm <t ≦ 0.4 mm, 0 <A × B / C ≦ 2.35.

Moreover, the compressor which concerns on this invention is equipped with the cylinder in which the compression chamber was formed inside, and the coupling pipe which is attached to the cylinder and communicates with the said compression chamber, The said cylinder penetrates into the said compression chamber from the side surface of the cylinder, And a cross-sectional oblong through-hole formed so that the long side direction is along the circumferential direction of the cylinder, wherein at least one end thereof is formed into a cross-sectional oblong, and one end thereof is press-fitted into the through-hole. In communication with the compression chamber, and in the state where the coupling pipe is pushed into the through hole, the wall surface of the coupling pipe, which is a flat portion in a state before being pushed into the through hole, is convex toward the outer peripheral side of the coupling pipe. It is transforming.

The compressor according to the present invention can prevent the flat portion of the coupling pipe from deforming to the inner circumferential side of the coupling pipe when the coupling pipe is pressed into the through hole of the cylinder. For this reason, the compressor according to the present invention can secure the practicality between the connecting pipe and the through-hole of the cylinder without using an elastic material such as an O-ring or a sealing tape, so that the gas leakage when compressing is performed. Can be prevented, and the performance of the compressor can be prevented from being lowered.

1 is a longitudinal sectional view showing a compressor according to an embodiment of the present invention.
2 is an enlarged view of an essential part (vertical section view) showing a compression part of a compressor according to an embodiment of the invention.
3 is a schematic diagram showing a gas suction hole formed in the cylinder of the compressor according to the embodiment of the present invention in comparison with a conventional gas suction hole;
Fig. 4 is a schematic diagram showing a modified form of both when press-fitting a coupling pipe of cross-section oblong to the gas suction hole of cross-section oblong.
5 is an explanatory diagram for explaining various dimensions in the vicinity of a suction hole;
6 is an explanatory diagram (vertical section view) for explaining a deformation direction of a suction pipe;
FIG. 7 is a characteristic diagram showing a result of CAE analysis when the thickness t of the coupling pipe in the embodiment of the invention is 1.6 mm. FIG.
The characteristic figure which shows the result of CAE analysis at the time of thickness t = 1mm of the coupling pipe in embodiment of this invention.
FIG. 9 is a characteristic diagram showing a result of CAE analysis when the thickness t of the coupling pipe in the embodiment of the invention is 0.4 mm. FIG.

1 is a longitudinal sectional view showing a compressor according to an embodiment of the present invention. 2 is an enlarged view of a main portion (vertical cross-sectional view) showing a compression portion of this compressor. 3 is a schematic diagram which shows the gas suction hole formed in the cylinder of this compressor compared with the conventional gas suction hole.

The compressor 1 which concerns on this embodiment is a multi-cylinder rotary compressor (two cylinder rotary compressor), and is provided with the shell 1a. Inside the shell 1a, a compression section, an electric motor section as a driving source of the compression section, and a rotating shaft 4 for transmitting the driving force of the motor section to the compression section are housed. The compressor 1 has a function of, for example, sucking and compressing a low-temperature gas refrigerant at the low pressure side of the refrigeration cycle circuit from the suction muffler 8 and discharging it from the discharge tube 9 as a high-pressure / high-temperature gas refrigerant. Have

To describe this in more detail, the electric motor portion is composed of an electric motor stator 21 fixed in the shell 1a and an electric motor rotor 22 shrink-fit to the rotary shaft 4, and is driven by being supplied with electric power from the outside. . Therefore, the glass terminal 10 used as a relay point of electric power supply is provided in the shell 1a.

The compression section includes a first bearing 6a, a second bearing 6b, a first cylinder 2a, a second cylinder 2b, a partition plate 3 and the like. In the first cylinder 2a, a roughly cylindrical through hole serving as a compression chamber is formed. In addition, a roughly cylindrical through-hole serving as a compression chamber is also formed in the second cylinder 2b. And these 1st cylinder 2a and the 2nd cylinder 2b are laminated | stacked in the direction along the center of the inner diameter of a compression chamber. In addition, when laminating | stacking the 1st cylinder 2a and the 2nd cylinder 2b, the partition plate 3 is arrange | positioned between them.

The 1st bearing part 6a is provided in the upper surface part of the 1st cylinder 2a, and closes the upper part of the compression chamber of the 1st cylinder 2a. That is, the airtightness of the compression chamber of the 1st cylinder 2a is ensured by the 1st bearing part 6a and the partition plate 3. Moreover, the 2nd bearing part 6b is provided in the lower surface part of the 2nd cylinder 2b, and closes the lower part of the compression chamber of the 2nd cylinder 2b. That is, the airtightness of the compression chamber of the 2nd cylinder 2b is ensured by the 2nd bearing 6b and the partition plate 3.

The rotating shaft 4 penetrates through the 1st bearing part 6a, the 1st cylinder 2a, the partition plate 3, the 2nd cylinder 2b, and the 2nd bearing part 6b which were laminated | stacked sequentially. This rotating shaft 4 is rotatably supported by the first bearing 6a and the second bearing 6b. Moreover, the 1st eccentric part 4a is formed in the rotation shaft 4 in the position corresponding to the 1st cylinder 2a, and the 2nd eccentric part 4b is formed in the position corresponding to the 2nd cylinder 2b. It is. These 1st eccentric part 4a and the 2nd eccentric part 4b are arrange | positioned at 180 degree shift | offset. In addition, a substantially cylindrical first piston 5a is rotatably provided in the first eccentric portion 4a, and a substantially cylindrical second piston 5b is rotatably provided in the second eccentric portion 4b.

The compression part is fixed in the shell 1a by press-fitting the 1st cylinder 2a to the shell 1a, for example. In addition, the motor stator 21 is also fixed, for example, by pressing or welding the motor stator 21 to the shell 1a.

In the 1st cylinder 2a, the vane (not shown) is provided freely, and this vane is pressed against the 1st piston 5a by a biasing means (not shown). When the rotating shaft 4 rotates by the electric motor part, the 1st piston 5a rotates in the 1st cylinder 2a. At this time, the vane follows the outer circumferential portion of the first piston 5a to divide the compression chamber into a low pressure space and a high pressure space. Similarly, also in the 2nd cylinder 2b, the vane is provided freely, and this vane is pressed against the 2nd piston 5b by a biasing means (not shown). When the rotating shaft 4 rotates by the electric motor part, the 2nd piston 5b rotates in the 2nd cylinder 2b. At this time, the vane follows the outer peripheral portion of the second piston 5b to divide the inside of the compression chamber into a low pressure space and a high pressure space.

In these 1st cylinder 2a and the 2nd cylinder 2b, the gas suction hole 11a (corresponding to the through-hole of this invention) which penetrates into a compression chamber from the side surface is formed. One end of the coupling pipe 12 is press-fitted into these gas suction holes 11a. In addition, the suction muffler 8 is connected to the other end of the coupling pipe 12. That is, the gas refrigerant flowing into the suction muffler 8 (that is, the refrigerant on the low pressure side of the refrigeration cycle circuit) is connected to the first cylinder 2a and the second through the coupling pipe 12 and the gas suction hole 11a. It is sucked into the compression chamber formed in the cylinder 2b. The refrigerant sucked into the compression chamber is compressed and discharged into the shell 1a from a valve (not shown) formed in the flange portions of the first bearing portion 6a and the second bearing portion 6b. The refrigerant discharged into the shell 1a flows out of the shell 1a from the discharge tube 9.

Moreover, in the compressor 1 which concerns on this embodiment, the guide pipe 13 used as the guide when the coupling pipe 12 is press-fitted into the gas suction hole 11a is provided in the outer peripheral surface of the shell 1a. .

Here, in the compressor 1 according to the present embodiment, as shown in Fig. 3A, the cross-sectional shape of the gas suction hole 11a formed in the first cylinder 2a and the second cylinder 2b is The shape of the manor (the shape which connected two circles of the same diameter by tangential line) is made. Moreover, the gas suction hole 11a is arrange | positioned so that the long side direction of cross-sectional oblong shape may follow the circumferential direction of the 1st cylinder 2a and the 2nd cylinder 2b. For this reason, the edge part of the side in which the coupling pipe 12 is press-fitted into the gas suction hole 11a also has the shape of a cross section of the shape corresponding to the gas suction hole 11a. For this reason, the compressor 1 which concerns on this embodiment is compared with the conventional compressor (refer FIG.3 (b)) in which the gas suction hole 11b of circular cross section was formed in the side surface of a cylinder, and the 1st cylinder 2a and the 1st Even if the thickness of the two cylinders 2b is made thin, the amount of refrigerant flowing into the compression chamber can be ensured, and a loss of suction pressure can be prevented. Therefore, the compressor 1 which concerns on this embodiment can be reduced in size, and can multi-call without increasing the capacity | capacitance of the shell 1a very much. Further, by reducing the thickness of the first cylinder 2a and the second cylinder 2b, the diameter of the compression chamber (cylinder inner circumferential surface), the first piston 5a, and the second piston 5b can be reduced without changing the compression chamber capacity. Since the diameter can be increased, it is possible to reduce refrigerant leakage (leakage loss) from the high pressure side space of the compression chamber to the low pressure side space.

However, when the coupling pipe 12 is press-fitted into the gas suction hole 11a, the strength of the vicinity of the gas suction hole 11a of the first cylinder 2a and the second cylinder 2b and the strength of the coupling pipe 12 are shown. Depending on the relationship between the first and second cylinders 2a and 2b, the actuality between the coupling pipe 12 and the coupling pipe 12 deteriorate, resulting in leakage of refrigerant from the location (gas leakage loss becomes large). Discarded).

Therefore, in the compressor 1 which concerns on this embodiment, the shape of the gas suction hole 11a vicinity in the 1st cylinder 2a and the 2nd cylinder 2b was comprised as follows.

In addition, since the shape of the vicinity of the gas suction hole 11a in the 1st cylinder 2a and the 2nd cylinder 2b is the same shape, the 1st cylinder 2a is demonstrated below.

FIG. 4: is a schematic diagram which shows the modified form of both when press-fitting the coupling pipe of cross section oblong into the gas suction hole of cross section oblong.

When the strength of the vicinity of the portion of the first cylinder 2a that is outside the straight portion of the gas suction hole 11a (hereinafter referred to as the cylinder flat portion 11c) and the strength of the coupling pipe 12 are balanced. As shown to Fig.4 (a), both the 1st cylinder 2a and the coupling pipe 12 are connected, without breaking down the cross-sectional shape of a rectangle. In this case, the coupling pipe 12 is in contact with the entire surface of the cylinder flat portion 11c, and the first cylinder 2a and the coupling pipe 12 are sealed without a gap.

In addition, when the strength near the cylinder flat part 11c of the 1st cylinder 2a is weaker than the strength of the coupling pipe 12, as shown to FIG. 4 (b), the cylinder flat part 11c and the coupling pipe will be shown. The flat portion of 12 is deformed so as to be convex toward the outer circumferential side of the coupling pipe 12. Even in this case, the coupling pipe 12 is in contact with the front surface of the cylinder flat portion 11c, and the space between the first cylinder 2a and the coupling pipe 12 is sealed without a gap.

However, when the strength near the cylinder flat portion 11c of the first cylinder 2a is stronger than the strength of the coupling pipe 12, as shown in Fig. 4C, the flat portion of the coupling pipe 12 is, It deforms so that it may become convex toward the inner peripheral side of the coupling pipe 12. In such a case, a gap is generated between the coupling pipe 12 and the cylinder flat portion 11c, and it becomes impossible to seal between the first cylinder 2a and the coupling pipe 12.

For this reason, in this embodiment, the shape of the vicinity of the gas suction hole 11a which the deformation | transformation form of the coupling pipe 12 becomes FIG. 4 (a) or FIG. 4 (b) was calculated | required by CAE analysis.

In detail, as shown in FIG. 5, the thickness of the cylinder flat part 11c is A, the long side direction length in the cross section of the gas suction hole 11a is short, and B is short in the cross section of the gas suction hole 11a. The longitudinal length was defined as C. And the deformation amount Y of the coupling pipe 12 was CAE analyzed by changing these A, B, C, the thickness t of the coupling pipe 12, and the press-fitting zone D.

As shown in FIG. 6 (a longitudinal cross-sectional view of the vicinity of the gas suction hole), the deformation amount of the coupling pipe 12 is a positive direction in the deformation direction in which the coupling pipe 12 is convex toward the outer circumferential side. The deformation | transformation direction which 12) becomes convex toward the inner peripheral side was made into the negative direction. In addition, the 1st cylinder 2a assumed the casting using cast iron, and assumed that the coupling pipe was iron, CAE analysis was performed.

7-9 is a characteristic diagram which shows the result of CAE analysis in embodiment of this invention. 7-9, the vertical axis | shaft is a deformation | transformation quantity of the coupling pipe 12, and the horizontal axis has shown AxB / C.

In detail, FIG. 7 is a characteristic diagram which shows the result of CAE analysis at the time of thickness t = 1.6 mm of the coupling pipe in embodiment of this invention.

The straight line E1 of FIG. 7 has a thickness A of the cylinder flat portion 11c and a gas suction hole under the condition that the press-fitting table D is 0.05 mm and the thickness t of the coupling pipe 12 is 1.6 mm. The relationship between the long side length B in the cross section of 11a, and the deformation amount Y of the coupling pipe 12 whose short side length C in the cross section of the gas suction hole 11a is an index was calculated | required. will be. Specifically, this relationship was obtained as follows. First, the press-fitting table D is fixed to 0.05 mm and the thickness t of the coupling pipe 12 to 1.6 mm, and the thickness A of the cylinder flat portion 11c and the cross section of the gas suction hole 11a are fixed. The long side length B and the short side length C in the cross section of the gas suction hole 11a were also changed appropriately, and the deformation amount Y of the coupling pipe 12 was determined by CAE analysis. And these deformation amounts Y were plotted on the graph, and the relationship mentioned above was calculated | required from these plot points.

In other words, this straight line E1 becomes the following relational expression (1).

In this relation 1, Y becomes 0 in AxB / C = 3.38. As a result, when the press-fitting table D is 0.05 mm and the thickness t of the coupling pipe 12 is 1.6 mm, when A × B / C = 3.38, the gas suction hole 11a of the first cylinder 2a is used. It can be seen that the modified form of the vicinity of the () and the coupling pipe 12 is shown in FIG. In addition, when AxB / C <3.38, the deformation | transformation form of the gas intake hole 11a of the 1st cylinder 2a, and the coupling pipe 12 becomes FIG.4 (b), and 1st cylinder 2a is shown. And it can be seen that the practicality of the coupling pipe 12 is secured. In addition, when A x B / C> 3.38, the modified form of the gas suction hole 11a of the first cylinder 2a and the coupling pipe 12 is shown in Fig. 4 (c), and the coupling pipe 12 and It can be seen that there is a gap between the cylinder flat portion 11c and that the gap between the first cylinder 2a and the coupling pipe 12 cannot be carried out.

The straight line F1 of FIG. 7 is cylinder flat part 11c by the same method as the straight line E1 on the condition that the press-fitting table D is 0.1 mm and the thickness t of the coupling pipe 12 is 1.6 mm. Coupling pipe 12 whose index A is the thickness A, the long side length B at the cross section of the gas suction hole 11a, and the short side length C at the cross section of the gas suction hole 11a. The relationship between strain amount Y of

This straight line F1 becomes the following relational expression 2.

In this relation 2, Y becomes 0 in AxB / C = 3.28. Thereby, when the press-fitting table D is 0.1 mm and the thickness t of the coupling pipe 12 is 1.6 mm, when AxB / C = 3.28, the gas suction hole 11a of the first cylinder 2a It can be seen that the modified form of the vicinity of the () and the coupling pipe 12 is shown in FIG. In addition, when AxB / C <3.28, the modified form of the gas suction hole 11a of the 1st cylinder 2a and the coupling pipe 12 becomes FIG. 4 (b), and the 1st cylinder 2a And it can be seen that the practicality of the coupling pipe 12 is secured. In addition, when A x B / C> 3.28, the deformation form of the gas intake hole 11a of the first cylinder 2a and the coupling pipe 12 is shown in Fig. 4 (c), and the coupling pipe 12 and It can be seen that there is a gap between the cylinder flat portion 11c and that the gap between the first cylinder 2a and the coupling pipe 12 cannot be carried out.

The straight line G1 of FIG. 7 has the cylinder flat part 11c by the same method as the straight line E1 on condition that the press-fitting table D is 0.15 mm and the thickness t of the coupling pipe 12 is 1.6 mm. Coupling pipe 12 whose index A is the thickness A, the long side length B at the cross section of the gas suction hole 11a, and the short side length C at the cross section of the gas suction hole 11a. The relationship between strain amount Y of

This straight line G1 becomes the following relational expression (3).

In this relation 3, Y becomes 0 in AxB / C = 3.2. As a result, when the press-fitting table D is 0.15 mm and the thickness t of the coupling pipe 12 is 1.6 mm, when A x B / C = 3.2, the gas suction hole of the first cylinder 2a It can be seen that the modified form of the vicinity of 11a and the coupling pipe 12 is shown in Fig. 4 (a), and the practicality of the first cylinder 2a and the coupling pipe 12 is secured. In addition, when AxB / C <3.2, the deformation form of the gas suction hole 11a of the 1st cylinder 2a and the coupling pipe 12 becomes FIG.4 (b), and the 1st cylinder 2a And it can be seen that the practicality of the coupling pipe 12 is secured. In addition, when A x B / C> 3.2, the modified form of the gas suction hole 11a of the first cylinder 2a and the coupling pipe 12 is shown in Fig. 4 (c), and the coupling pipe 12 and It can be seen that there is a gap between the cylinder flat portion 11c and that the gap between the first cylinder 2a and the coupling pipe 12 cannot be carried out.

8 is a characteristic diagram which shows the result of CAE analysis at the time of thickness t = 1mm of the coupling pipe in embodiment of this invention.

The straight line E2 of FIG. 8 is a cylinder with the same method as the straight line E1 of FIG. 7, under the condition that the press-fitting table D is 0.05 mm and the thickness t of the coupling pipe 12 is 1 mm. The thickness A of the flat part 11c, the long side length B in the cross section of the gas suction hole 11a, and the short side length C in the cross section of the gas suction hole 11a as an index. The relationship between the deformation amount Y of the coupling pipe 12 is calculated | required.

This straight line E2 becomes the following relational expression 4.

In this relation 4, Y becomes 0 in AxB / C = 2.88. As a result, when the press-fitting table D is 0.05 mm and the thickness t of the coupling pipe 12 is 1 mm, when A x B / C = 2.88, the gas suction hole 11a of the first cylinder 2a is used. It can be seen that the modified form of the vicinity of the () and the coupling pipe 12 is shown in FIG. In addition, when AxB / C <2.88, the deformation | transformation form of the gas suction hole 11a of the 1st cylinder 2a, and the coupling pipe 12 becomes FIG.4 (b), and 1st cylinder 2a is shown. And it can be seen that the practicality of the coupling pipe 12 is secured. In addition, when A x B / C> 2.88, the deformation form of the gas suction hole 11a of the first cylinder 2a and the coupling pipe 12 is shown in Fig. 4 (c), and the coupling pipe 12 and It can be seen that there is a gap between the cylinder flat portion 11c and that the gap between the first cylinder 2a and the coupling pipe 12 cannot be carried out.

The straight line F2 of FIG. 8 is cylinder flat by the method similar to the straight line E1 of FIG. 7, under the condition that the press-fitting table D is 0.1 mm and the thickness t of the coupling pipe 12 is 1 mm. Coupling using the thickness A of the part 11c, the long side length B in the cross section of the gas suction hole 11a, and the short side length C in the cross section of the gas suction hole 11a as an index. The relationship between the deformation amount Y of the pipe 12 is obtained.

This straight line F2 becomes the following relational expression 5.

In this relation 5, Y becomes 0 in AxB / C = 2.83. As a result, when the press-fitting table D is 0.1 mm and the thickness t of the coupling pipe 12 is 1 mm, when A x B / C = 2.83, the gas suction hole 11a of the first cylinder 2a is provided. It can be seen that the modified form of the vicinity of the () and the coupling pipe 12 is shown in FIG. In addition, when AxB / C <2.83, the deformation | transformation form of the gas intake hole 11a of the 1st cylinder 2a, and the coupling pipe 12 becomes FIG.4 (b), and 1st cylinder 2a is shown. And it can be seen that the practicality of the coupling pipe 12 is secured. In addition, when A x B / C> 2.83, the deformation form of the gas suction hole 11a of the first cylinder 2a and the coupling pipe 12 is shown in Fig. 4 (c), and the coupling pipe 12 and It can be seen that there is a gap between the cylinder flat portion 11c and that the gap between the first cylinder 2a and the coupling pipe 12 cannot be carried out.

The straight line G2 of FIG. 8 is cylinder flat by the method similar to the straight line E1 of FIG. 7, under the condition that the press-fitting table D is 0.15 mm and the thickness t of the coupling pipe 12 is 1 mm. Coupling using the thickness A of the part 11c, the long side length B in the cross section of the gas suction hole 11a, and the short side length C in the cross section of the gas suction hole 11a as an index. The relationship between the deformation amount Y of the pipe 12 is obtained.

This straight line G2 becomes the following relational expression 6.

In this relation 6, Y becomes 0 at AxB / C = 2.8. As a result, in the case where the press-fitting table D is 0.15 mm and the thickness t of the coupling pipe 12 is 1 mm, when A x B / C = 2.8, the gas suction hole of the first cylinder 2a It can be seen that the modified form of the vicinity of 11a and the coupling pipe 12 is shown in Fig. 4 (a), and the practicality of the first cylinder 2a and the coupling pipe 12 is secured. In addition, when AxB / C <2.8, the deformation form of the gas intake hole 11a of the 1st cylinder 2a and the coupling pipe 12 becomes FIG.4 (b), and 1st cylinder 2a is shown. And it can be seen that the practicality of the coupling pipe 12 is secured. In addition, when A x B / C> 2.8, the modified form of the gas intake hole 11a of the 1st cylinder 2a and the coupling pipe 12 becomes FIG.4 (c), and the coupling pipe 12 and It can be seen that there is a gap between the cylinder flat portion 11c and that the gap between the first cylinder 2a and the coupling pipe 12 cannot be carried out.

9 is a characteristic diagram which shows the result of CAE analysis when the thickness t of a coupling pipe in embodiment of this invention is 0.4 mm.

The straight line E3 of FIG. 9 has a cylinder similar to the straight line E1 of FIG. 7 under the condition that the press-fitting table D is 0.05 mm and the thickness t of the coupling pipe 12 is 0.4 mm. The thickness A of the flat part 11c, the long side length B in the cross section of the gas suction hole 11a, and the short side length C in the cross section of the gas suction hole 11a as an index. The relationship between the deformation amount Y of the coupling pipe 12 is calculated | required.

This straight line E3 becomes the following relational formula (7).

In this relation 7, Y becomes 0 in AxB / C = 2.38. As a result, when the press-fitting table D is 0.05 mm and the thickness t of the coupling pipe 12 is 0.4 mm, when A × B / C = 2.38, the gas suction hole 11a of the first cylinder 2a is used. It can be seen that the modified form of the vicinity of the () and the coupling pipe 12 is shown in FIG. In addition, when AxB / C <2.38, the deformation form of the gas suction hole 11a of the 1st cylinder 2a and the coupling pipe 12 becomes FIG.4 (b), and the 1st cylinder 2a And it can be seen that the practicality of the coupling pipe 12 is secured. In addition, when A x B / C> 2.38, the deformation form of the gas suction hole 11a of the first cylinder 2a and the coupling pipe 12 is shown in Fig. 4 (c), and the coupling pipe 12 and It can be seen that there is a gap between the cylinder flat portion 11c and that the gap between the first cylinder 2a and the coupling pipe 12 cannot be carried out.

The straight line F3 of FIG. 9 is cylinder flat by the method similar to the straight line E1 of FIG. 7, under the condition that the press-fitting table D is 0.1 mm and the thickness t of the coupling pipe 12 is 0.4 mm. Coupling using the thickness A of the part 11c, the long side length B in the cross section of the gas suction hole 11a, and the short side length C in the cross section of the gas suction hole 11a as an index. The relationship between the deformation amount Y of the pipe 12 is obtained.

This straight line F3 becomes the following relational expression (8).

In this relation 8, Y becomes 0 in AxB / C = 2.37. As a result, when the press-fitting table D is 0.1 mm and the thickness t of the coupling pipe 12 is 0.4 mm, when A x B / C = 2.37, the gas suction hole 11a of the first cylinder 2a is used. It can be seen that the modified form of the vicinity of the () and the coupling pipe 12 is shown in FIG. In addition, when AxB / C <2.37, the modified form of the gas suction hole 11a of the 1st cylinder 2a and the coupling pipe 12 becomes FIG.4 (b), and the 1st cylinder 2a is shown. And it can be seen that the practicality of the coupling pipe 12 is secured. In addition, when A x B / C> 2.37, the deformation form of the gas suction hole 11a of the first cylinder 2a and the coupling pipe 12 is shown in Fig. 4 (c), and the coupling pipe 12 and It can be seen that there is a gap between the cylinder flat portion 11c and that the gap between the first cylinder 2a and the coupling pipe 12 cannot be carried out.

The straight line G3 of FIG. 9 is cylinder flat by the method similar to the straight line E1 of FIG. 7, under the condition that the press-fitting table D is 0.15 mm and the thickness t of the coupling pipe 12 is 0.4 mm. Coupling using the thickness A of the part 11c, the long side length B in the cross section of the gas suction hole 11a, and the short side length C in the cross section of the gas suction hole 11a as an index. The relationship between the deformation amount Y of the pipe 12 is obtained.

This straight line G3 becomes the following relational expression (9).

In this relation 9, Y becomes 0 in AxB / C = 2.35. Thereby, when the press-fitting table D is 0.15 mm and the thickness t of the coupling pipe 12 is 0.4 mm, when AxB / C = 2.35, the gas suction hole of the first cylinder 2a It can be seen that the modified form of the vicinity of 11a and the coupling pipe 12 is shown in Fig. 4 (a), and the practicality of the first cylinder 2a and the coupling pipe 12 is secured. In addition, when AxB / C <2.35, the deformation form of the gas suction hole 11a of the 1st cylinder 2a and the coupling pipe 12 becomes FIG.4 (b), and the 1st cylinder 2a is shown. And it can be seen that the practicality of the coupling pipe 12 is secured. In addition, when A x B / C> 2.35, the deformation form of the gas suction hole 11a of the first cylinder 2a and the coupling pipe 12 is shown in Fig. 4 (c), and the coupling pipe 12 and It can be seen that there is a gap between the cylinder flat portion 11c and that the gap between the first cylinder 2a and the coupling pipe 12 cannot be carried out.

That is, from FIG. 7 to FIG. 9 and the above-described relations 1 to 9, the smaller the press-fitting table D (in other words, the smaller the deformation load applied to the flat portion of the coupling pipe 12), the more A × B / It can be seen that C increases. Moreover, it turns out that AxB / C becomes large, so that the thickness of the coupling pipe 12 is thick (in other words, the strength of the flat part is strong in the coupling pipe 12). More specifically, when the press-fitting table D is 0.05 mm or less (0 <D≤0.05mm), when the thickness t of the coupling pipe 12 is 0mm <t≤1.6mm, 0 <A × When B / C ≦ 3.38, and the thickness t of the coupling pipe 12 is 0 mm <t ≦ 1 mm, 0 <A × B / C ≦ 2.88 and the thickness t of the coupling pipe is 0. In the case of mm <t ≦ 0.4mm, it is understood that by setting 0 <A × B / C ≦ 2.38, the first cylinder 2a and the coupling pipe 12 can be secured. In addition, when the press-fitting table D is 0.1 mm or less (0 <D≤0.1mm), when the thickness t of the coupling pipe 12 is 0mm <t≤1.6mm, it is 0 <AxB / C ≤ 3.28, and when the thickness t of the coupling pipe 12 is 0 mm <t ≤ 1 mm, 0 <A x B / C ≤ 2.83, and the thickness t of the coupling pipe is 0 mm <t In the case of ≤ 0.4 mm, it can be seen that by setting 0 <A x B / C ≤ 2.37, the first cylinder 2a and the coupling pipe 12 can be secured. In addition, when the press-fitting table D is 0.15 mm or less (0 <D≤0.15mm), when the thickness t of the coupling pipe 12 is 0mm <t≤1.6mm, it is 0 <AxB / C ≤ 3.2, the thickness t of the coupling pipe 12 is 0 mm <t ≤ 1 mm, 0 <A x B / C ≤ 2.8, and the thickness t of the coupling pipe is 0 mm <t In the case of ≤ 0.4 mm, it can be seen that by setting 0 <A x B / C ≤ 2.35, the actuality of the first cylinder 2a and the coupling pipe 12 can be secured.

As mentioned above, in the compressor 1 comprised like this embodiment, even if the thickness of the 1st cylinder 2a and the 2nd cylinder 2b is made thin, the amount of refrigerant which flows into a compression chamber can be ensured, The loss can be prevented. Therefore, the compressor 1 which concerns on this embodiment can be reduced in size, and can multi-call without increasing the capacity | capacitance of the shell 1a very much. Further, by reducing the thickness of the first cylinder 2a and the second cylinder 2b, the diameter of the compression chamber (cylinder inner circumferential surface), the first piston 5a, and the second piston 5b can be reduced without changing the compression chamber capacity. Since the diameter of the can be increased, the refrigerant leakage (leakage loss) from the high pressure side space of the compression chamber to the low pressure side space can be reduced. Then, the gas suction hole (a) or the deformation shape of the coupling pipe 12 in the vicinity of the gas suction hole 11a of the first cylinder 2a and the second cylinder 2b is 4 (a) or 4 (b). Since the shape around 11a) is defined, gas leakage between the gas suction hole 11a and the coupling pipe 12 which is concerned can also be prevented without using an elastic material such as an O-ring or seal tape, It can also prevent that the performance of the compressor 1 resulting from the gas leakage from the said location falls.

In addition, the compressor 1 demonstrated by this embodiment is an example to the last. The compression unit is not limited to the two cylinder type, but may be a single type. The mechanism of the compression section is not limited to a rotary type, but various mechanisms such as a vane type can be adopted. It is of course possible to provide a multistage compressor in which a plurality of compression units are provided and the refrigerant is sequentially compressed. The compressor 1 may of course be a low pressure shell compressor in which the shell 1a is filled with a low pressure gas refrigerant. That is, the effect shown in Embodiment 1 can be acquired by defining the cross-sectional shape of the through-hole formed in the side surface of a cylinder, and the connection pipe which communicates with a compression chamber press-fitted as mentioned above.

1: Compressor
1a: shell
2a: first cylinder
2b: second cylinder
3: partition plate
4: axis of rotation
4a: first eccentric part
4b: second eccentric
5a: first piston
5b: second piston
6a: first bearing part
6b: second bearing part
8: suction muffler
9: discharge tube
10: glass terminal
11a: gas suction hole (cross section shape)
11b: gas suction hole (conventionally, in cross section)
11c: cylinder flat part
12: joining pipe
13: guide pipe
21: motor stator
22: electric motor rotor

Claims (10)

A cylinder having a compression chamber formed therein,
A coupling pipe attached to the cylinder and communicating with the compression chamber,
The cylinder penetrates the compression chamber from the side surface of the cylinder, and a through-hole having a cross-sectional oblong shape is formed so that the long side direction is along the circumferential direction of the cylinder,
The coupling pipe has at least one end portion formed in a cross-sectional oblong shape, one end portion of which is pressed into the through hole by 0.05 mm or less and communicates with the compression chamber,
A, the length of the cylinder in the cross section of the through hole A, the length of the long side direction in the cross section of the through hole B, and the through state, before the coupling pipe is pressed into the through hole. If the short side length in the cross section of the hole is defined as C,
When the thickness t of the said coupling pipe is 0 mm <t <= 1.6 mm,
0 <A × B / C≤3.38
Compressor characterized in that the. The method of claim 1,
When the thickness t of the said coupling pipe is 0 mm <t <= 1 mm,
0 <A × B / C≤2.88
Compressor characterized in that the. 3. The method according to claim 1 or 2,
When the thickness t of the said coupling pipe is 0 mm <t <= 0.4 mm,
0 <A × B / C≤2.38
Compressor characterized in that the. A cylinder having a compression chamber formed therein,
A coupling pipe attached to the cylinder and communicating with the compression chamber,
The cylinder penetrates the compression chamber from the side surface of the cylinder, and a through-hole having a cross-sectional oblong shape is formed so that the long side direction is along the circumferential direction of the cylinder,
The coupling pipe has at least one end portion formed in a cross-sectional oblong shape, one end portion of which is press-fitted into the through hole by 0.1 mm or less and communicates with the compression chamber,
A, the length of the cylinder in the cross section of the through hole A, the length of the long side direction in the cross section of the through hole B, and the through state, before the coupling pipe is pressed into the through hole. If the short side length in the cross section of the hole is defined as C,
When the thickness t of the said coupling pipe is 0 mm <t <= 1.6 mm,
0 <A × B / C≤3.28
Compressor characterized in that the. 5. The method of claim 4,
When the thickness t of the said coupling pipe is 0 mm <t <= 1 mm,
0 <A × B / C≤2.83
Compressor characterized in that. The method according to claim 4 or 5,
When the thickness t of the said coupling pipe is 0 mm <t <= 0.4 mm,
0 <A × B / C≤2.37
Compressor characterized in that the. A cylinder having a compression chamber formed therein,
A coupling pipe attached to the cylinder and communicating with the compression chamber,
The cylinder penetrates the compression chamber from the side surface of the cylinder, and a through-hole having a cross-sectional oblong shape is formed so that the long side direction is along the circumferential direction of the cylinder,
The coupling pipe has at least one end portion formed in a cross-sectional oblong shape, one end portion of which is pressed into the through hole by 0.15 mm or less and communicates with the compression chamber,
A, the length of the cylinder in the cross section of the through hole A, the length of the long side direction in the cross section of the through hole B, and the through state, before the coupling pipe is pressed into the through hole. If the short side length in the cross section of the hole is defined as C,
When the thickness t of the said coupling pipe is 0 mm <t <= 1.6 mm,
0 <A × B / C≤3.2
Compressor characterized in that the. 8. The method of claim 7,
When the thickness t of the said coupling pipe is 0 mm <t <= 1 mm,
0 <A × B / C≤2.8
Compressor characterized in that the. 9. The method according to claim 7 or 8,
When the thickness t of the said coupling pipe is 0 mm <t <= 0.4 mm,
0 <A × B / C≤2.35
Compressor characterized in that the. A cylinder having a compression chamber formed therein,
A coupling pipe attached to the cylinder and communicating with the compression chamber,
The cylinder penetrates the compression chamber from the side surface of the cylinder, and a through-hole having a cross-sectional oblong shape is formed so that the long side direction is along the circumferential direction of the cylinder,
The coupling pipe has at least one end portion formed in a cross-sectional oblong shape, and one end portion thereof is pressed into the through hole to communicate with the compression chamber.
In the state where the coupling pipe is pressed into the through hole,
The compressor is characterized in that the wall surface of the coupling pipe, which is a flat portion in the state before being pushed into the through hole, is deformed so as to be convex toward the outer peripheral side of the coupling pipe.

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