KR20070009958A - Rotary type two stage compressor - Google Patents

Abstract

A rotary two stage compressor is provided to improve the productivity by easily performing pressing strokes of a low pressure suction pipe, a middle discharge pipe, and a high pressure suction pipe. A rotary two stage compressor includes a motor, a rotary shaft(2), a rotary compression element, a middle space, a plurality of through-holes, a low pressure suction pipe(38), a middle discharge pipe, a high pressure suction pipe(41), and a cylindrical connection pipe(43). The low pressure suction pipe is communicated with a low pressure compression element. The middle discharge pipe is communicated with the middle space. The high pressure suction pipe is communicated with the high pressure compression element. The connection pipe makes contact with the low pressure suction pipe, the middle discharge pipe, and the high pressure suction pipe. The connection pipe has an outer diameter on the inner side which is smaller than the outer diameter on the outside so as to follow the appearances of the low pressure suction pipe, the middle discharge pipe, and the high pressure suction pipe.

Description

Rotary two stage compressor {ROTARY TYPE TWO STAGE COMPRESSOR}

1 is a longitudinal sectional view of a rotary two stage compressor showing one embodiment of the present invention;

FIG. 2 is a cross-sectional view A-A of the rotary two stage compressor shown in FIG. 1; FIG.

3 is a front view of the rotary two-stage compressor shown in FIG. 1 and FIG.

Figure 4 is a longitudinal sectional view of a rotary two stage compressor showing one embodiment of the present invention.

Fig. 5 is a front view of the trunk portion of the rotary two stage compressor shown in Fig. 4;

Fig. 6 is a longitudinal sectional view of a rotary two stage compressor showing one embodiment of the present invention.

FIG. 7 is a sectional view taken along the line A-A of the rotary two stage compressor shown in FIG.

8 is a configuration diagram of an injection cycle using the rotary two-stage compressor shown in FIG.

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

1: compressor

2: axis of rotation

13: airtight container

20: compression element

22: torso

25: inlet

27: discharge tube

38: low pressure suction pipe

39: discharge pipe for intermediate

40: intermediate tube

41: high pressure suction tube

43: connection tube

45: injection pipe

[Document 1] Japanese Patent Laid-Open No. 60-128990

The present invention relates to a rotary two stage compressor for use in an air conditioner with a refrigeration cycle.

BACKGROUND ART Conventionally, in a rotary two-stage compressor used for a refrigeration cycle, for example, a structure disclosed in Japanese Patent Application Laid-open No. 60-128990 (hereinafter referred to as Patent Document 1) is known. The compressor in this prior art is equipped with the electric motor which consists of a stator and a rotor in the upper part in a sealed container. The rotating shaft connected to the motor has two eccentric parts. In the compression mechanism corresponding to the eccentric portion, a high pressure compression element and a low pressure compression element are provided inside the sealed container in order from the motor side.

Each compression element orbits the rotor by eccentric rotation of the eccentric portion of the rotation axis. The eccentric part is 180 degrees out of phase, and the phase difference of the compression process of each compression element is 180 degrees. In other words, the compression process of the two compression elements is out of phase.

The gas refrigerant, the working fluid, is sucked into the low pressure compression element at low pressure Ps, and is compressed to rise to the medium pressure Pm. At this time, it is sucked from the low pressure suction pipe passing through the through hole provided in the sealed container and communicating with the low pressure compression element.

The gas refrigerant discharged from the low pressure compression element at the intermediate pressure Pm is discharged from the intermediate space provided in the sealed container to the intermediate flow path. At that time, it is discharged into the intermediate flow path from the intermediate discharge pipe passing through the through hole provided in the sealed container and communicating with the intermediate space.

The medium pressure Pm gas refrigerant is then sucked into the high pressure compression element via the intermediate flow path and compressed to high pressure Pd. At this time, it is sucked from the high pressure suction pipe passing through the through hole provided in the sealed container and communicating with the high pressure compression element.

The low pressure suction tube, the intermediate discharge tube, and the high pressure suction tube are press-fitted by an apparatus such as a press from the outside of the sealed container to ensure sealing performance with the pump portion, and then joined by the sealed container and welding.

The high pressure (Pd) gas refrigerant discharged from the compressor is condensed in the condenser and then decompressed to the low pressure in the expansion mechanism. It is then evaporated in the evaporator to become a gas refrigerant and drawn into the low pressure compression element.

[Patent Document 1] Japanese Unexamined Patent Publication No. 60-128990 (Page 5, Fig. 1)

The rotary two-stage compressor described in the technical field to which the invention belongs and the prior art in that field is not clearly described with respect to the positional relationship of the three through holes provided in the sealed container. According to the drawings, the through holes of the low pressure suction pipe and the high pressure suction pipe and the through hole for the intermediate discharge pipe are opened in the reverse direction with respect to the axis center of the rotating shaft. For this reason, the shape of the intermediate | middle pipe which connects a high pressure suction pipe and an intermediate | middle discharge pipe becomes complicated, and there existed a problem that fluid loss increased.

Moreover, in the prior art example of the background art, it is necessary to press-fit in at least two directions. In other words, the press-in stroke is required twice. In addition, even in the case of welding the sealed container, the low pressure suction pipe, the intermediate discharge pipe, and the high pressure suction pipe, there is a problem that the welding operation is complicated because the welding direction is different.

An object of the present invention is to provide a high performance and easy to manufacture compressor that solves the above-mentioned problems.

In order to achieve the above object, the rotary compressor of the present invention includes an electric motor in a sealed container, a rotary shaft driven by the electric motor and having two eccentric parts, and two compression chambers installed through a partition plate through which the rotary shaft penetrates. The hermetic container in communication with a low pressure compression element and a high pressure compression element each having a roller which is orbitally moved by eccentric rotation, and a compression chamber of the low pressure compression element and a compression chamber of the high pressure compression element. A middle space spaced apart from an inner space of the plurality of through holes provided in a columnar shape along a longitudinal direction of the rotary shaft provided in the sealed container, and a low pressure suction pipe passing through the through holes to communicate with the low pressure compression element; And an intermediate discharge tube communicating with the intermediate space through another through hole, and through another through hole. And a high pressure suction tube communicating with the high pressure compression element.

In addition, in the case of installing an accumulator having a long axis in the same direction as the rotational axis of the electric motor, an approximately L-shaped suction tube communicating the accumulator and the low pressure suction tube, and an approximately U-shaped communication tube communicating the intermediate discharge tube and the high pressure suction tube, It is preferable that an intermediate tube is provided and the major axis of the accumulator and the arrangement axis of the through holes are at different angles as seen from the axis of rotation of the axis of rotation.

When the through-holes are in close proximity, the through-holes are externally provided with a substantially cylindrical connecting tube inscribed to the low-pressure suction pipe, the intermediate discharge pipe, or the high-pressure suction pipe, respectively. The outer diameter of the suction tube, the intermediate discharge tube, or the high pressure suction tube has a shape having a different diameter with the inner portion smaller than the outer portion with respect to the sealed container, and the connection tube includes the low pressure suction tube, the intermediate discharge tube, Alternatively, the outer diameter of the inner part may have a shape having a different diameter smaller than the outer diameter of the outer part with respect to the sealed container so as to conform to the outer shape of the high pressure suction pipe.

Embodiments of the present invention will be described with reference to the drawings. That is, in FIG. 1, the compressor 1 has the airtight container 13 which consists of the bottom part 21, the cover part 12, and the trunk | drum 22. As shown in FIG. Above the inside of the airtight container 13, the electric motor 14 which has the stator 7 and the rotor 8 is provided. The rotating shaft 2 connected to the electric motor 14 is provided with two eccentric parts 5, and is journaled to the main bearing 9 and the sub bearing 19. As shown in FIG. The main bearing 9 which has the end plate part 9a in order from the electric motor 14 side with respect to the rotating shaft 2, the high pressure compression element 20b, the intermediate | middle partition board 15, and the low pressure compression element 20a. And the sub-bearing 19 provided with the end plate portion 19 are stacked and integrated with a fastening element (not shown) such as a bolt.

The end plate portion 9a is fixed to the inner wall of the trunk portion 22 by welding to support the main bearing 9. The end plate portion 19a is supported by the sub bearing 19. In addition, in this embodiment, although the end plate part 19a is being fixed by the bolt etc., you may fix it to the trunk | drum 22 by welding.

Each compression element 20a, 20b is comprised as follows. Representatively in FIG. 2 is a cross-sectional view of the A-A cross section of FIG. 1, ie the compression element 20a for low pressure. In the low pressure compression element 20a, the sub-bearing 19, the cylindrical cylinder 10a, the cylindrical roller 11a fitted to the outer circumference of the eccentric portion 5a, and the intermediate partition plate 15 The compression chamber 23a is comprised.

Moreover, in the high pressure compression element 20b, the main bearing 9, the cylindrical cylinder 10b, the cylindrical roller 11b fitted to the outer periphery of the eccentric part 5b, and the intermediate | middle partition board Compression chamber 23b is comprised by 15. As shown in FIG. In these compression chambers 23a and 23b, as shown in Fig. 2, the flat-shaped ben 18 connected by the pressing force applying means 17 such as the coil spring is adapted to the eccentric motion of the eccentric portions 5a and 5b. The compression chambers 23a and 23b are divided into a compression space and a suction space by advancing and moving in contact with the outer circumference of the rotating rollers 11a and 11b.

The compression element 20 drives the roller 11 by the eccentric portion 5 rotating eccentrically. As shown in Fig. 1, the eccentric portion 5a and the eccentric portion 5b are 180 degrees out of phase, and the phase difference in the compression process of the compression elements 20a and 20b is 180 degrees. In other words, the compression process of the two compression elements is out of phase.

The flow of the gas refrigerant which is the working fluid is shown by the arrow in FIG. The gas refrigerant of low pressure (ps) supplied through the pipe 31 flows through the accumulator 36, the intake pipe 37, and the low pressure suction pipe 38 in order. Then, the gas refrigerant at low pressure Ps is sucked into the low pressure compression element 20a from the suction port 25a, and the roller 11a is eccentrically rotated to be compressed to the intermediate pressure Pm.

When the discharge valve 28a opened when the pressure in the compression chamber 23a reaches a preset pressure is opened at the intermediate pressure Pm, the discharge space in which the gas refrigerant at the intermediate pressure Pm communicates with the discharge port 26a ( 33). The discharge space 33 is a space spaced from the sealed space 29 in the sealed container 13 by the sub-bearing 19 and the cover 35, and the internal pressure thereof is an intermediate pressure Pm. The refrigerant gas in the discharge space 33 flows through the intermediate discharge tube 39, the intermediate tube 40, and the high pressure suction tube 41, and is sucked into the high pressure compression element 20b from the suction port 25b.

The gas refrigerant of medium pressure Pm sucked into the high pressure compression element 20b from the suction port 25b is compressed to high pressure Pd by the revolving roller 11b. When the discharge valve 28b opened when the pressure in the compression chamber 23b reaches a predetermined pressure is opened at a high pressure Pd, the gas refrigerant flows from the discharge port 26 into the sealed space 29 which is an internal space of the sealed container 13. To be discharged. The gas refrigerant discharged into the sealed space 29 passes through the gap of the electric motor 14 and is discharged by the discharge tube 27.

Next, Fig. 3 shows a side view from the direction B in Figs. 1 and 2. The low pressure suction pipe 36, the intermediate discharge pipe 39, and the high pressure suction pipe 41 pass through the cylindrical through-hole 42 formed in the body portion 22 by pressing or drilling, respectively, and the cylinder 10a. ) And the sub bearing 19 and the cylinder 10b are press-fitted and connected to each other by a press or the like. The through holes 42 are formed in one row in the longitudinal direction of the trunk portion 22, that is, in the rotation direction of the rotation shaft 2 shown in FIG. 1. Here, the through-hole 42 was provided with the connection pipe 43 of the substantially cylindrical shape which inscribes with the low pressure suction pipe 36, the intermediate discharge pipe 39, and the high pressure suction pipe 41, respectively.

The suction pipe 37 connecting the accumulator 36 and the low pressure suction pipe 37 has a positional relationship in which the inlet and the outlet are twisted as shown in Figs. That is, it has a substantially L shape in the plane perpendicular | vertical to the rotation direction of the rotating shaft 2. The intermediate pipe 40 connecting the intermediate discharge pipe 39 and the high pressure suction pipe 41 has an approximately U shape. These tubes are all connected by welding.

In addition, as shown in FIG. 2, the accumulator 36 has the long axis whose angle is different from the arrangement direction of the through-hole 42 from the shape of the intake pipe 37. As shown in FIG. The angle difference was 20 degrees or more.

Since the inlet pipe 37 is approximately L, the intermediate pipe 40 can connect the intermediate discharge pipe 39 and the high pressure suction pipe 41 in a U shape without forming a conventional complicated shape. For this reason, the flow distance of the gas refrigerant which matched the intake pipe 37 and the intermediate pipe 40 can be shortened, and fluid loss is reduced. 2, the outermost circumference of the intermediate tube 40 can be made smaller than the outermost circumference of the accumulator 36, and the compactness is also excellent.

Further, since the through holes 42 are formed in a line, the low pressure suction pipe 38, the intermediate discharge pipe 39, and the high pressure suction pipe 41 can be press-fitted from one direction as shown by arrow C in FIG. Therefore, the press-in stroke can be simplified. Welding of the through-hole 42 and the connection pipe 43 or the connection pipe 43 and the low pressure suction pipe 38, the intermediate discharge pipe 39, and the high pressure suction pipe 41 can also be welded from one direction. As a result, administration such as positioning can be simplified. Moreover, since the angle difference between the intermediate pipe 40 and the accumulator 36 is 20 degrees or more, workability at the time of welding is also excellent. By these effects, the present invention can improve the productivity after reducing the fluid loss of the pipe.

Next, the application example of the present invention will be described with reference to Figs. In the application example, the low pressure suction pipe 38, the intermediate discharge pipe 39, and the high pressure suction pipe 41 have an outer diameter Φ d of the inside of the body portion 22, and an outer diameter Φ D of the outside of the body portion 22. Molding smaller than. That is, they were molded to different diameters by throttling or expansion. Similarly, the connecting tube 43 also has an outer diameter inside the body portion 22 smaller than the outside diameter, and is shaped according to the shapes of the low pressure suction pipe 38, the intermediate discharge pipe 39, and the high pressure suction pipe 41. It was made.

For this reason, even if phi d is restricted by the dimensions of the cylinder 10 or the sub bearing 19, phi D can be freely enlarged, so that the fluid loss in the pipe portion can be reduced. In addition, since the through hole diameter Φd 'provided in the trunk portion 22 can be made smaller than that between the same ΦD and the through holes 43, the trunk portion 22 shown by the broken line in FIG. The cross-sectional area between the through holes 43 can be increased, and the internal pressure of the sealed container 13 can be improved.

In addition, as shown in Figs. 4 and 5, by protruding and molding the portion 44 for forming the through hole 43, the pressure resistance at which deformation can be controlled by the internal pressure of the airtight container 13 is improved. .

Next, the application example of this invention is demonstrated using FIG. 6, FIG. In this application example, the injection pipe 45 is installed in the intermediate pipe 40. As shown in FIG. 7, the injection pipe 45 is installed in the opposite direction to the accumulator 36 with respect to the central axis of the intermediate pipe 40 as seen from the upper surface of the compressor 1. The outer diameter of the injection pipe 45 is smaller than the outer diameter of the intermediate pipe 40, and the attachment position is provided so as to be close to the high pressure suction pipe 41. In addition, the height of the injection pipe 45 was set so that it might become upper than the end plate part 9a.

The injection cycle of the application example is demonstrated using FIG. This air conditioner is an injection cycle. The refrigerant gas of the high pressure Pd discharged from the rotary two-stage compressor 1 to which the present invention is applied is condensed in the condenser 3, and then expanded in the first expansion mechanism 4a, and is pressurized to an intermediate pressure Pm. This is depressurized. This reduced pressure refrigerant is separated into gas and liquid in the gas-liquid separator 6. The separated liquid refrigerant is further depressurized to the low pressure Ps in the second expansion mechanism 4b downstream of the gas-liquid separator 6, and then evaporated in the evaporator 16 to become a gas refrigerant. The low pressure (Ps) gas refrigerant is sucked into the low pressure compression element 20a from the suction port 25a, and the roller 11a fitted to the eccentric portion 5a revolves to be compressed to the intermediate pressure Pm, so that the intermediate tube 40 To be discharged.

The gas refrigerant of the intermediate tube 40 is mixed with the gas refrigerant of intermediate pressure Pm induced from the injection tube 45 in which the gas-liquid separator 6 and the intermediate flow path 30 communicate. Thereafter, the gas refrigerant of medium pressure Pm sucked into the high pressure compression element 20 from the suction port 25b is compressed to the high pressure Pd by the revolving roller 11b fitted to the eccentric portion 5b. It is discharged from the discharge tube 27.

Since the injection cycle bypasses the gas refrigerant having low heat transfer performance in the evaporator 16, the excess circulation flow rate to the low pressure side compression element 20a is reduced to reduce the compression work, thereby reducing the coefficient of performance of the air conditioner. Improve the COP.

In the present application example, as shown in Figs. 6 and 7, the injection pipe 45 is provided in the opposite direction of the accumulator 36, so that the thermal movement between the two can be controlled to enable stable operation. Moreover, the said arrangement | positioning is excellent also in the weldability and workability of the injection pipe 45 or the accumulator 45.

According to the present invention, the fluid loss in the intermediate tube can be reduced, and the press-in stroke of the low pressure suction tube, the intermediate discharge tube, and the high pressure suction tube can be facilitated, and the productivity can be improved. In addition, by setting the connecting pipe to a different diameter, the pressure resistance is improved after securing the above advantages.

Claims (2)

In an airtight container, an electric motor, a rotary shaft driven by the electric motor and having two eccentric portions, and two compression chambers provided through a partition plate through which the rotary shaft penetrates are provided with rollers orbiting by eccentric rotation of the eccentric portions, respectively. A rotary compression element having a low pressure compression element and a high pressure compression element, an intermediate space in communication with the compression chamber of the low pressure compression element and the compression chamber of the high pressure compression element and spaced apart from the interior space of the hermetic container; A plurality of through holes provided in a column shape along the longitudinal direction of the rotary shaft provided in the container, a low pressure suction pipe passing through the through holes to communicate with the low pressure compression element, and communicating with the intermediate space through other through holes. An intermediate discharge tube, a high pressure suction tube passing through another through hole, and communicating with the high pressure compression element; Contact with the outer through-hole, and a substantially cylindrical connection tube inscribed in each of the low-pressure suction pipe, the intermediate discharge pipe, or the suction line for the high pressure for, The outer diameter of the low pressure suction tube, the intermediate discharge tube, or the high pressure suction tube has a shape in which the inner portion is smaller in diameter than the outer portion with respect to the sealed container, and the connection tube is the low pressure suction tube and the intermediate grade. A rotary two-stage compressor having a shape in which the outer diameter of the inner portion is smaller than the outer diameter of the outer portion of the sealed container so as to conform to the outer shape of the discharge tube or the suction tube for high pressure. The rotary two-stage compressor according to claim 1, further comprising a substantially U-shaped intermediate tube communicating the intermediate discharge tube and the high pressure suction tube.

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