WO2016206054A1

WO2016206054A1 - Rotary compressor and refrigerating cycle device having same

Info

Publication number: WO2016206054A1
Application number: PCT/CN2015/082376
Authority: WO
Inventors: 小津政雄; 向卫民; 张�诚; 宋鹏杰; 王玲
Original assignee: 广东美芝制冷设备有限公司
Priority date: 2015-06-25
Filing date: 2015-06-25
Publication date: 2016-12-29

Abstract

A rotary compressor and a refrigeration cycle device having same. The rotary compressor is located in a closed housing (1). The closed housing accommodates a motor part (6) composed of a stator (7) fixed in the housing (1) and a rotor (8) rotating with a certain air gap kept from a inner surface of the stator (7), a compression mechanism section (4) comprising a crankshaft (10) and a rolling piston (66) rotating through the rotor (8), at least two supporting components (15, 28) supporting the compression mechanism section (4) rotating repeatedly and a buffer component (32) limiting the range of the repeated rotating. A suction pipe (50) or an exhaust pipe (51) communicated with the compression mechanism section (4) is in sliding fit with the housing (1). The suction pipe (50) or the exhaust pipe (51) opens to an additional closed chamber (55) on the housing (1).

Description

Rotary compressor and refrigeration cycle device therewith

Technical field

The present invention relates to the field of refrigeration, and more particularly to a rotary compressor and a refrigeration cycle apparatus therewith.

Background technique

The world's popular rotary compressors are composed of single or double cylinders, of which more than 90% are single cylinders. On the other hand, compared to the double cylinder, the single cylinder is greatly affected by the compression torque. This rotational vibration, particularly in window air conditioners and car air conditioners, has not only vibration problems but also noise problems, which have been expected to be improved a long time ago.

The vibration of a rotary compressor is composed of vibrations of two components, one is rotational vibration and the other is revolution vibration due to the unbalanced mass of the piston. The latter can be placed in the rotor with a balance block. However, the former is difficult to solve in principle and has become a long-term issue.

Summary of the invention

The present invention aims to solve at least one of the technical problems in the related art to some extent.

To this end, the present invention proposes a rotary compressor that can effectively reduce rotational vibration.

The present invention also proposes a refrigeration cycle apparatus having the above rotary compressor.

According to the rotary compressor of the embodiment of the present invention, a motor unit that is fixed in the casing and a rotor that is rotated by maintaining a constant air gap between the inner circumference of the stator and a rotor is provided in the sealed casing. a compression mechanism portion of the crankshaft and the rolling piston that rotates the rotor, at least two support members that support the compression mechanism portion that repeatedly rotates, and a buffer member that restricts the repeated rotation range, and a suction pipe that communicates with the compression mechanism portion Or the exhaust pipe is slidably coupled to the casing, and the suction pipe or the exhaust pipe opens to an additional closed cavity on the casing.

According to the rotary compressor of the embodiment of the present invention, since the compression mechanism portion is reciprocally provided in the casing, and the repeated rotation of the compression mechanism portion is buffered by the cushioning member, the repeated rotational vibration of the compression mechanism portion can be prevented from being transmitted to the casing. The rotary vibration of the rotary compressor can be effectively reduced, and the fatigue disconnection of the motor lead wire of the motor portion and the contact with the housing can be avoided.

In some embodiments of the invention, the two support members are located on either side of the rotor.

In some embodiments of the invention, the cushioning member is a coil spring that expands and contracts following repeated rotation of the compression mechanism portion.

In some embodiments of the invention, the suction tube or the exhaust tube opens to a muffler that is in communication with a compression chamber that houses the rolling piston.

In some embodiments of the invention, one of the support members is slidably engaged with the crankshaft.

A refrigeration cycle apparatus according to an embodiment of the present invention includes: a rotary compressor according to the above embodiment of the present invention; a condenser and an evaporator, the closed chamber connecting the evaporator or the condenser.

According to the refrigeration cycle apparatus of the embodiment of the invention, the vibration can be reduced by providing the above-described rotary compressor.

In a further embodiment of the invention, the closed chamber is configured as a reservoir or an oil separator.

DRAWINGS

Figure 1 is a longitudinal sectional view showing the inside of a rotary compressor in connection with Embodiment 1;

Figure 2 is a detailed view of the compression mechanism portion associated with the first embodiment;

Figure 3 is a detailed view of the coil spring associated with the first embodiment;

Figure 4 is a detailed view of the compression mechanism portion associated with the second embodiment;

Figure 5 is a longitudinal sectional view showing the inside of a low-pressure rotary compressor of the casing, relating to the third embodiment;

Figure 6 is a longitudinal sectional view of a rotary compressor having a liquid storage device in connection with Embodiment 4;

Figure 7 is a longitudinal sectional view of a rotary compressor having an oil separator, relating to Embodiment 5;

Figure 8 is a longitudinal sectional view showing the inside of a horizontal rotary compressor in connection with Embodiment 6.

Reference mark:

Rotary compressor 1, housing 2, A housing 2a, B housing 2b, C housing 2c, D housing 2d, motor portion 6, stator 7, air gap 9, rotor 8, motor coil 7a, L balance block 8a, S balance block 8b, motor lead line 81,

Compression mechanism portion 4, cylinder 62, compression chamber 65, rolling piston 66, main bearing 60, sub-bearing 20, internal muffler 25, gas inlet and outlet pipe 50, suction port 20a, muffler chamber 25a, exhaust hole 60a, exhaust valve 60b, round protrusion 26,

The crankshaft 10, the main shaft 11, the countershaft 12, the eccentric shaft 13, the small diameter shaft 11a,

Cylindrical plate 28, spindle holding plate 15, bushing 16, sealing ring 52, A hook 33a, B hook 33b,

Coil spring 32, coil 32c, operating end 32a (32b),

Three-core terminal 80, gas inlet and outlet pipe 51, external muffler 55, external connection pipe 56, open end 56a, oil pool 3, oil hole 3a (71a), main bearing frame 35, O-ring 53, arc welding spot 36, cylinder a frame 71, an oil separating member 73, an oil injection pipe 74, a liquid refrigerant injection pipe 75,

A heat exchanger 101, expansion device 102, B heat exchanger 103, accumulator 104 (70), oil separator 105 (72).

detailed description

Embodiments of the invention are described in detail below, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the drawings are intended to be illustrative of the invention and are not to be construed as limiting.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", " After, "Left", "Right", "Vertical", "Horizontal", "Top", "Bottom", "Inside", "Outside", "Clockwise", "Counterclockwise", "Axial", The orientation or positional relationship of the "radial", "circumferential" and the like is based on the orientation or positional relationship shown in the drawings, and is merely for convenience of description of the present invention and simplified description, and does not indicate or imply the indicated device or component. It must be constructed and operated in a particular orientation, and is not to be construed as limiting the invention.

Moreover, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, features defining "first" or "second" may include at least one of the features, either explicitly or implicitly. In the description of the present invention, the meaning of "a plurality" is at least two, such as two, three, etc., unless specifically defined otherwise.

A rotary compressor 1 according to an embodiment of the present invention will be described in detail below with reference to Figs. The rotary compressor 1 can be applied to a refrigerating cycle device, which can be an air conditioner, a refrigerating/freezing machine, or a water heater.

According to the rotary compressor 1 of the embodiment of the present invention, in the hermetic casing 2, the stator 7 fixed in the casing 2 and the rotor 8 which maintains a certain air gap 9 and rotates between the inner circumference of the stator 7 are accommodated. The motor unit 6 includes a compression mechanism unit 4 that includes a crankshaft 10 that rotates by the rotor 8 and a rolling piston 66, at least two support members that support the compression mechanism unit 4 that repeatedly rotates, and a cushioning member that limits the range of repeated rotation.

The suction pipe or the exhaust pipe that communicates with the compression mechanism unit 4 is slidably engaged with the casing 2, and the suction pipe or the exhaust pipe opens to the sealed cavity added to the casing 2.

That is, the rotary compressor 1 includes a housing 2, a motor portion 6, a compression mechanism portion 4, at least two support members, a buffer member, and a gas inlet and outlet pipe 50, wherein the motor portion 6 includes a stator 7 and a rotor 8, and the stator 7 is fixed On the inner wall of the casing 2, a certain air gap 9 is maintained between the rotor 8 and the inner circumference of the stator 7.

The compression mechanism portion 4 includes a crankshaft 10 that cooperates with the rotor 8 to be rotated by the rotor 8 and a rolling piston 66 that drives the rolling piston 66 to rotate. At least two branch members support the compression mechanism portion 4 to position the compression mechanism portion 4 in the casing 2, and the compression mechanism portion 4 is repetitively located in the casing 2, and the cushioning member limits the repeated rotation range of the compression mechanism portion 4, the gas The inlet and outlet pipe 50 is slidably engaged with the casing 2, and the gas inlet and outlet pipe 50 opens to the additional sealed chamber on the casing 2. When the rotary compressor 1 is the low-pressure rotary compressor 1 in the casing, the gas inlet and outlet pipe 50 is an exhaust pipe. When the rotary compressor 1 is the high-pressure rotary compressor 1 in the casing, the gas inlet and outlet pipe 50 is a suction pipe.

According to the rotary compressor 1 of the embodiment of the present invention, since the compression mechanism portion 4 is reciprocally provided in the casing 2, and the repeated rotation of the compression mechanism portion 4 is buffered by the cushioning member, repeated rotational vibration of the compression mechanism portion 4 can be avoided. The transmission to the casing 2 can effectively reduce the rotational vibration of the rotary compressor 1, and at the same time, the fatigue disconnection of the motor lead wire of the motor portion 6 and the contact with the casing 2 can be avoided.

In some embodiments of the invention, two support members are located on either side of the rotor 8. In some examples of the invention, one of the support members slides with the crankshaft 10. For example, as shown in FIGS. 1 and 2, the two support members may include a cylindrical plate 28 and a spindle retaining plate 15, and the circular projection 26 of the compression mechanism portion 4 projects into the cylindrical plate 28 and is slidably engaged with the cylindrical plate 28, the spindle. The retaining plate 15 is provided with a bushing 16 which is fitted over the main shaft 11 of the crankshaft 10 and is slidably engaged with the main shaft 11. In the example of FIG. 4, the inner wall of the casing 2 is provided with a main bearing frame 35, and the main bearing 60 is slidably supported on the main bearing frame 35. It will of course be understood that it is also possible that the cylinder 62 or the sub-bearing 20 is slidably supported on the main bearing frame 35.

Specifically, the cushioning member is a coil spring 32 that expands and contracts following the repeated rotation of the compression mechanism portion 4.

In some embodiments of the invention, the suction or exhaust pipe opens to a muffler (i.e., internal silencer 25 described below) that communicates with the compression chamber 65 housing the rolling piston 66. That is, the muffler is in communication with the compression chamber 65, and the suction pipe or the exhaust pipe opens to the muffler, so that noise can be further reduced.

A refrigeration cycle apparatus according to an embodiment of the present invention includes: a rotary compressor 1, a condenser, and an evaporator according to the above-described embodiment of the present invention, the closed chamber being connected to an evaporator or a condenser.

According to the refrigeration cycle apparatus of the embodiment of the invention, by providing the rotary compressor 1 described above, the vibration can be reduced.

In a further embodiment of the invention, the closed chamber is configured as a reservoir or an oil separator. For example, as shown in FIG. 6, the sealed chamber is a reservoir 70. As shown in FIG. 7, the sealed chamber is an oil separator 72.

A rotary compressor according to several embodiments of the present invention will be described in detail below with reference to Figs.

Example 1:

The motor unit 6 and the compression mechanism unit 4 are housed in the casing 2 of the rotary compressor 1 shown in Fig. 1 . The motor unit 6 is composed of a stator 7 fixed to the inner circumference of the casing 2 and a rotor 8 that rotates by maintaining a constant air gap 9 between the inner diameters of the stators 7. The rotor 8 is a main shaft 11 of the crankshaft of the components of the compression mechanism unit 4. Fixed at the place. Further, a motor coil 7a is provided in the stator 7.

Like the motor of the conventional rotary compressor, the motor unit 6 is selected from an AC motor and a DC inverter motor that can change the rotational speed. For reference, the air gap is about 0.4 to 0.5 mm when mounted on a domestic air conditioner rotary compressor, and high precision concentricity is required between the rotor 8 and the inner diameter of the stator 7.

The compression mechanism portion 4 is a rolling piston 66 and a sliding piece (not shown) housed in the compression chamber 65 formed in the cylinder 62, and a main bearing 60 and a sub-bearing fixed to both end opening faces of the compression chamber 65. 20, a crankshaft 10 coupled thereto, and an internal muffler 25 fixed to the bottom surface of the sub-bearing 20, a gas inlet and outlet pipe 50 connected to the center of the internal muffler 25, and a rotor 8 fixed at the main shaft 11 of the crankshaft 10 .

As shown in FIG. 2, the compression mechanism portion 4 is supported by a cylindrical plate 28 fixed by the C housing 2c and a bushing 16 held by the spindle support plate 15. A rolling bearing can also be used for the bushing 16. a coil spring having an outer circumference of the cylindrical plate 28 32 is a cushioning device of the compression mechanism unit 4, and not only the load of the compression mechanism unit 4 but also the rotation angle of the compression mechanism unit 4 is determined.

FIG. 3 shows the coil spring 32. The left picture is a side view and the right picture is a plan view. The coil spring 32 is composed of a central coil 32c and an operating end 32a and an operating end 32b at both ends thereof, and is freely changeable according to the opening angle of the two operating ends of the compression mechanism portion 4.

In FIG. 2, the crankshaft 10 is composed of a main shaft 11, a counter shaft 12, and an eccentric shaft 13. A part of the shaft end of the main shaft 11 is a small diameter shaft 11a which is slidably engaged with the bushing 16 held by the spindle support plate 15. While securing the motor gap 9 described above, the spindle support plate 15 of the fixed cylindrical plate is welded at the inner diameter of the casing 2. The suction hole 20a provided in the sub-bearing 20 is opened in the compression chamber 65 and the muffler chamber 25a. On the other hand, the exhaust hole 60a opened in the main bearing 60 is opened and closed by the exhaust valve 60b, and is a gas passage through which the high-pressure gas of the compression chamber 65 is discharged into the upper space of the main bearing 60.

The L balance block 8a and the S balance block 8b provided on both end faces of the rotor 8 are masses which cancel out the total unbalanced rotation mass of the rolling piston 66 and the eccentric shaft 13 which are eccentrically rotated by the crankshaft 10. Theoretically, by making them equal, the revolution of the rotary compressor 1 is zero. Therefore, in order to reduce the total vibration of the rotary compressor 1, it is an object of the present invention to reduce the rotational vibration of the rotary compressor 1 caused by the torque variation of the compression chamber 65.

Next, the assembly process of the compression mechanism portion 4 and the stator 7 in the inside of the casing 2 will be briefly described.

The A housing 2a and the C housing 2c of the assembled cylindrical body are welded. The cylinder 28 is inserted from the upper end of the opened A casing 2a, and the inner diameter of the cylindrical plate 28 and the inner diameter of the A casing 2a are aligned, and the bottom surface of the cylindrical plate 28 is welded and fixed at the center of the C casing 2c. Thereafter, the seal ring 52 is embedded in the center opening of the cylindrical plate 28. Next, the inner side of the coil spring 32 is inserted into the outer circumference of the cylindrical plate 28. The operating end 32a of the coil spring 32 is inserted into the U groove of the A hook 33a.

Next, the circular projection 26 of the compression mechanism portion 4 is inserted into the cylindrical plate 28. At this time, the fixed gas inlet and outlet pipe 50 is press-fitted into the center of the circular projection 26 in advance, and is fitted into the seal ring 52. At the same time, the operating end 32b of the coil spring 32 is fitted into the U groove to which the B hook 33b is fixed. Next, the side surface of the A casing 2a is heated all the way, and the stator 7 is inserted into the heat jacket assembly. At this time, the rotor 8 is embedded in the inner diameter of the stator 7.

Next, the outer diameter of the rotor 8 and the inner diameter of the stator 7 are adjusted, and the bushing 16 integrated with the main shaft support plate 15 is fitted into the outer diameter of the small diameter shaft 11a. At the same time, the inner circumference of the A casing 2a is welded to the outer diameter of the main shaft support plate 15. After that, the alignment jig that removes the rotor 8 and the stator 7 assembles the motor lead wire 81 at the three-core terminal 80 of the B casing 2b. Finally, the B casing 2b having the gas inlet and outlet pipe 51 is welded and fixed at the A casing 2a.

After the assembly described above, the gas inlet and outlet pipe 50 projecting through the center of the C casing 2c through the inner diameter of the seal ring 52 is opened to the external muffler 55 fixed in the C casing 2c in advance. Further, the external muffler 55 is connected to the external muffler 55. Further, in accordance with the assembly work described above, the A casing 2a and the C casing 2c may be deep-drawn integrated casings. Further, in the above-described assembly process, the assembly method in which the outer diameter of the main shaft support plate 15 is spot-welded at the inner circumference of the A casing 2a, and the assembly of the A casing 2a in the C casing 2c is also applicable.

The internal pressure of the casing 2 in the operation of the compressor is the high pressure side, but since the pressure of the muffler chamber 25a is the low pressure side, the pressure of the gas inlet and outlet pipe 50 and the external muffler 55 is the low pressure side. The seal ring 52 prevents gas leakage from the casing 2 to the external muffler 55 by the pressure difference. In other words, it has the same effect as an O-ring.

Further, the inner diameter of the seal ring 52 is equal to the outer diameter of the gas inlet and outlet pipe 50, but the outer diameter of the cylindrical portion of the seal ring 52 has a certain amount of play with respect to the center hole of the C casing 2c. That is, even if the concentricity of the gas inlet and outlet pipe 50 and the crankshaft 10 is slightly inferior in accuracy, the rotation of the gas inlet and outlet pipe 50 is not affected, and the gas leakage from the seal ring 52 is not affected.

In the operation of the rotary compressor 1, the compression mechanism portion 4 is repeatedly rotated within a designed angular range. Similarly, since the gas inlet and outlet pipe 50 is also repeatedly rotated, there is no wear between the gas inlet and outlet pipe 50 and the seal ring 52. For this reason, the gas inlet and outlet pipe 50 is a steel pipe, but the seal ring 52 is a highly reliable PEEK, PTFE material or the like. Further, as shown in Fig. 2, since the oil hole 3a opens the cylindrical plate 28, the seal ring 52 is in a sufficient lubricating oil. Thus, gas leakage and abrasion from the casing 2 to the external muffler 55 can be sufficiently prevented.

The repeated rotation angle of the compression mechanism unit 4 is proportional to the change in the compression torque of the compression chamber 65, and is inversely proportional to the mass and the rotation speed of the compression mechanism unit 4. Based on these data, the design of the coil spring 32 is optimized. The pipe connected to the compression mechanism portion 4 is only the gas inlet and outlet pipe 50 that rotates in the compression mechanism portion 4, and its structure is axisymmetric with respect to the axial center (crankshaft).

Therefore, the repeated rotation angle of the compression mechanism portion 4 can be several times more than the reciprocating piston compressor of the same class to which the exhaust pipe and the lead wire are connected. That is to say, the compression mechanism portion 4 that is rotatably separated from the stator 7 has a large degree of freedom in design of the damper device, and the advantage of reducing the rotational vibration is optimized.

Shown in Figure 1 is a description of the flow of refrigerant after the refrigerant has been sealed in the refrigeration cycle. The low-pressure refrigerant sucked from the external connection pipe 56 flows in the order of the external muffler 55, the gas inlet and outlet pipe 50, and the muffler chamber 25a, and is sucked into the compression chamber 65 from the suction hole 20a. The high-pressure refrigerant compressed in the compression chamber 65 is discharged from the exhaust hole 60a, moves to the upper portion of the motor through the outer circumferential groove of the stator 7, and the air gap 9, and is discharged from the gas inlet and outlet pipe 51.

The high-pressure refrigerant that has moved to the A heat exchanger 101 passes through the expansion device 102 to become a low-pressure refrigerant, and the B heat exchanger 103 evaporates from the accumulator 104 to return to the external muffler to constitute a circulation system. In addition, the internal pressure of the casing 2 is the high pressure side. The gas inlet and outlet pipe 50 corresponds to a suction pipe, the gas inlet pipe 51 corresponds to an exhaust pipe, the A heat exchanger 101 corresponds to a condenser, and the B heat exchanger 103 corresponds to an evaporator.

The fluctuation of the compression torque generated in the compression chamber 65 is the repeated rotational vibration of the compression mechanism portion 4, but the vibration of the coil 32 prevents the propagation of the casing 2. Here, since the casing 2 is fixed by the heaviest stator 7, it is advantageous for preventing vibration propagation to the casing 2. Moreover, the microvibration of the housing 2 can improve the propagation to the device side by the anti-vibration rubber pad.

Since the compression mechanism portion 4 and the stator are separated, the rotation of the compression mechanism portion 4 is repeated, and the motor coil 7a has Some motor lead wires 81 are not vibrating. Therefore, there is no fear of fatigue disconnection of the motor lead wire 81 during operation and contact with the casing 2.

In addition, since the cylindrical plate 28, the coil spring 32, and the circular protrusion 26 are in oil, it is advantageous for abrasion and sliding sound. Further, the vertical movement of the compression mechanism portion 4 generated during transportation of the apparatus is improved by adjusting the gap between the cylindrical plate 28 and the circular projection 26 and the gap between the upper end of the main shaft 11 and the bushing 16.

The arrangement of the coil springs 32 can be adopted in the manner of a small reciprocating piston compressor. For example, it is also easy to determine the rotation angle of the compression mechanism portion 4 by the plurality of coil springs in the outer peripheral portion of the main bearing 60. As shown in this example, the size from the rotation axis of the compression mechanism unit 4 is increased, and when the coil spring is disposed, the spring constant can be reduced, and the spring can be downsized.

The lower end of the crankshaft 10 of the present invention, that is, the lower end of the countershaft 12 is not opened in the oil pool 3. Due to this feature, a centrifugal pump penetrating the conventional crankshaft cannot be used. Therefore, the present invention directly applies oil to each sliding surface of the crankshaft using a vane pump or a differential pressure pump. The present invention can apply oil to each sliding surface of the crankshaft by any means in the prior art, for example, as in Patent Document 1 (CN201110273673.0), an oil groove is provided on the eccentric shaft and at least between the eccentric shaft and the main bearing, in the sliding chamber and A communication passage is disposed between the oil pools, and a fluid mechanism that changes the fluid resistance by changing the flow direction of the fluid is disposed in the communication passage, and the oil in the oil pool passes through the fluid mechanism into the oil tank through the reciprocating motion of the sliding piece. Further, for example, as disclosed in Patent Document 2 (CN201110060473.7), a fuel supply pipe is connected to the transverse hole of the flange portion of the sub-bearing, and a sub-bearing oil groove is provided on the sub-bearing, and an eccentric shaft oil groove is provided on the outer diameter of the eccentric shaft, and the main bearing A spiral groove is arranged on the oil tank, and the oil in the oil pool is discharged from the lower port of the oil supply pipe to the auxiliary bearing oil groove, and then passes through the eccentric shaft oil groove and the spiral groove. Also, horizontal rotary compressors disclose several types of oil pumps that can be used.

Example 2:

The present invention is based on the gist of changing the design from the viewpoints of improvement in performance, reliability, and manufacturability. In the compression mechanism portion 4 shown in Fig. 4, the outer circumference of the main bearing 60 is fitted into the main bearing frame 35 provided in the inner circumference of the A casing 2a. As a result, the compression mechanism unit 4 can be freely rotated by the two supporting methods by the crankshaft 10 supported by the bushing 16. Moreover, the third support method was formed by adding the circular protrusion support method used in Example 1. Further, instead of the main bearing 60, the outer circumference of the cylinder 62 may be circular as a supporting means.

In the second embodiment, the coil spring 32 provided between the C casing 2c and the circular projection 26 supports the load of the compression mechanism portion 4, and serves as a cushioning device for determining the angular velocity of the rotation. Further, the gas inlet and outlet pipe 50 is welded to the C casing 2c to open to the muffler chamber 25a. That is, the gas inlet and outlet pipe 50 may be fixed to the C casing 2c.

The gap between the outer diameter of the gas inlet and outlet pipe 50 and the inner diameter of the circular projection 26 is necessary to make it larger in order to avoid direct contact therebetween. Here is a design example in which the above gap is sealed by the O-ring 53. The main bearing frame 35 is fixed to the inner circumference of the A casing 2a by three arc welding points 36 after adjusting the air gap 9. In other words, along The assembly process of the conventional compression mechanism. Further, since the crankshaft 10 is supported by the main bearing 60 and the bushing 16, the countershaft 12 used in the first embodiment can be omitted.

Example 3:

In FIG. 5, the suction hole 20a and the exhaust hole 60a which open the compression chamber 65 are each provided in the main bearing 60 and the sub-bearing 20. In other words, the components in which the suction hole 20a and the exhaust hole 60a are disposed are replaced with the first or second embodiment.

In the operation of the rotary compressor 1, the low-pressure refrigerant sucked from the gas inlet and outlet pipe 51 passes through the motor unit 6 from above and down, and is sucked by the suction hole 20a. The high-pressure refrigerant compressed in the compression chamber 65 is discharged to the muffler chamber 25a through the exhaust hole 60a, and then flows from the gas inlet and outlet pipe 50 to the external muffler 55, and flows out to the external connection pipe 56. Therefore, the internal pressure of the casing 2 becomes the low pressure side of the refrigeration cycle, and the muffler chamber 25a and the gas inlet and outlet pipe 50 and the external connection pipe 56 are the high pressure side. Thus, the configuration of the seal ring 52 is opposite to that of the embodiment 1.

The high-pressure refrigerant discharged from the external connection pipe 56 usually flows in the order of the B heat exchanger 103, the expansion device 102, and the A heat exchanger 101 from the oil separator 105 necessary for the low-pressure rotary compressor of the casing. Therefore, the flow direction of the refrigerant of

Embodiment

1 or 2 is opposite. In addition, if the housing is low pressure, no accumulator is needed.

As such, regardless of whether the pressure of the casing 2 is a high pressure type or a low pressure type, the present invention has an easily adaptable feature. In addition, in order for the pressure of the housing 2 to be the low pressure side, the slider back pressure must be the high pressure side. However, the swinging rotary compressor in which the rolling piston and the slider are integrated is not necessary. Since the design of the high pressure side of the back pressure of the slider has revealed many examples from the past, it is omitted here.

Example 4:

This is a design that expands the external muffler 55 (Fig. 1) with the desired capacity of the reservoir 70 at the bottom of the housing 2.

In Fig. 6, the reservoir 70 to which the D casing 2d is additionally sealed is welded to the outside of the C casing 2c. Therefore, the gas inlet and outlet pipe 50 is opened to the fixed cylindrical frame 71 fixed in the center of the D casing 2 in advance. The low-pressure refrigerant flowing out of the B heat exchanger 103 flows into the inside of the accumulator 70 from the external connection pipe 56.

The heavy-weight liquid refrigerant that flows in from the open end 56a of the inner peripheral opening of the D casing 2d is rotated on the outer peripheral side of the accumulator. A gas refrigerant having a low specific gravity is collected around the cylindrical frame 71, and is sucked from the gas inlet and outlet pipe 50 by the muffler chamber 25. The oil accumulated in the bottom of the accumulator 70 flows from the oil hole 71a opened in the cylindrical frame 71 and the gas refrigerant to the muffler chamber 25a.

Further, by adding the accumulator 70, the noise generated in the compression mechanism portion is also double-insulated. Therefore, not only vibration but also noise can be greatly reduced.

Example 5:

As in the fourth embodiment, the design of the accumulator 70 having the required capacity of the outer muffler 55 (Fig. 1) at the bottom of the casing 2 is expanded.

In Fig. 7, the gas inlet and outlet pipe 50 is previously opened to the oil separation member 73 fixed to the center portion of the D casing 2d. The oil mixed in the high-pressure refrigerant discharged from the gas inlet and outlet pipe 50 is trapped by the oil separator 73 and accumulated at the bottom of the oil separator 72. The oil injection pipe 74, which is opened in the compression chamber 65, returns the trapped oil to the compression chamber 65. The oil that cannot be returned to the compression chamber 65 and the high-pressure refrigerant are discharged from the external connection pipe 56 to the B heat exchanger 103, and become the amount of oil discharged in the circulation system. The oil separator 72 may be an oil separator of the prior art. For example, as disclosed in Patent Document 3 (CN201410053384.3), the oil separator may include a perforated plate having a through hole penetrating the perforated plate in the thickness direction, which is porous. The plate is fixed to the bottom of the D casing 2d and defines a separation chamber between the D casing 2d. The oil separator may also include a diffuser plate that causes the refrigerant to diffuse within the separation chamber. The diffusing plate may be a rotating body and the cross-sectional area of the diffusing plate may be gradually decreased from the top to the bottom, and the diffusing plate is disposed on the perforated plate. Or the density of a portion of the perforated plate may be greater than the density of the remainder of the perforated plate, the portion of the perforated plate being configured as a diffuser plate.

Example 6

Disclosed in Embodiment 4 is a design in which a vertical rotary compressor is changed to a horizontal rotary compressor. In Fig. 8, the compression mechanism portion 4 rotates around the rotation axis of the crankshaft 10, but since the rotation angle thereof is at most within ±30 degrees, the oil scattered by the oil is disturbed with respect to the rotor 8 that rotates at a high speed. There is a lot less oil flying. Thus, the present invention is also applicable even to a horizontal rotary compressor.

Further, the liquid refrigerant injection pipe 75 that connects the cylindrical frame 71 absorbs the liquid refrigerant and oil accumulated in the bottom of the accumulator, and is mixed into the gas refrigerant of the gas inlet and outlet pipe 50.

Industrial use possibilities

The rotary compressor disclosed in the present invention is mounted on an air conditioner, a refrigerating/freezing machine, a water heater, a refrigerating air conditioner for a vehicle, and the like.

In summary, we can see that

The invention solves the problem:

In the conventional rotary compressor, the compression mechanism portion and the stator that drives the compression mechanism portion are fixed in one sealed casing. As a result, the fluctuation of the compression torque of the compression mechanism unit directly becomes the vibration of the rotary compressor, and is transmitted to the vibration of the machine in which the rotary compressor is mounted.

Means to solve the above problems:

(1) Separating the compression mechanism portion of the crankshaft including the fixed rotor from the casing of the fixed stator. On the other hand, the compression mechanism portion is connected to the casing by two supporting means and a buffering means that allow rotation. (2) The internal muffler chamber that connects the compression chamber and the suction tube that is freely rotatably connected (in the case of the housing high pressure type) or the exhaust pipe (in the case of the housing low pressure type) It coincides with the rotation axis of the compression mechanism unit. Thus, the compression mechanism portion can be rotated. The rotation vibration of the compression mechanism portion is greatly reduced by the absorption by the buffer device.

The beneficial effects of the invention:

(1) It is possible to reduce the rotational vibration of a rotary compressor which is considered to be difficult.

(2) It is not only a single cylinder, but also a multi-cylinder rotary compressor.

(3) The internal pressure of the casing can be applied both on the high pressure side and the low pressure side, and may also be applied in a horizontal rotary compressor.

(4) The accumulator and oil separator are easy to set at the same time. The effect is that the noise is also greatly reduced.

(5) Since it does not require a highly difficult technique, it is excellent in manufacturability.

In the present invention, the terms "installation", "connected", "connected", "fixed" and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. Or in one piece; it may be a mechanical connection, or it may be an electrical connection or a communication with each other; it may be directly connected or indirectly connected through an intermediate medium, and may be an internal connection of two elements or an interaction relationship between two elements. Unless otherwise expressly defined. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.

In the present invention, the first feature "on" or "under" the second feature may be a direct contact of the first and second features, or the first and second features may be indirectly through an intermediate medium, unless otherwise explicitly stated and defined. contact. Moreover, the first feature "above", "above" and "above" the second feature may be that the first feature is directly above or above the second feature, or merely that the first feature level is higher than the second feature. The first feature "below", "below" and "below" the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.

In the description of the present specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" and the like means a specific feature described in connection with the embodiment or example. A structure, material or feature is included in at least one embodiment or example of the invention. In the present specification, the schematic representation of the above terms is not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples. In addition, various embodiments or examples described in the specification, as well as features of various embodiments or examples, may be combined and combined.

Although the embodiments of the present invention have been shown and described, it is understood that the above-described embodiments are illustrative and are not to be construed as limiting the scope of the invention. The embodiments are subject to variations, modifications, substitutions and variations.

Claims

A rotary compressor in which a stator fixed in a casing and a motor portion including a rotor that maintains a constant air gap between the inner circumference of the stator and a rotor are housed in a sealed casing a compression mechanism portion of the crankshaft and the rolling piston that rotates the rotor, at least two support members that support the compression mechanism portion that repeatedly rotates, and a buffer member that limits the repeated rotation range.

A suction pipe or an exhaust pipe that communicates with the compression mechanism portion is slidably engaged with the casing, and the suction pipe or the exhaust pipe opens to a sealed chamber added to the casing.
The rotary compressor according to claim 1, wherein said two support members are located on both sides of said rotor.
The rotary compressor according to claim 1, wherein the cushioning member is a coil spring that expands and contracts following repeated rotation of the compression mechanism portion.
The rotary compressor according to claim 1, wherein the suction pipe or the exhaust pipe opens to a muffler that communicates with a compression chamber that houses the rolling piston.
A rotary compressor according to claim 1, wherein one of said support members is slidably engaged with said crankshaft.
A refrigeration cycle device, comprising:

A rotary compressor according to any one of claims 1 to 5;

A condenser and an evaporator, the closed chamber connecting the evaporator or the condenser.
The refrigeration cycle apparatus according to claim 6, wherein the closed chamber is configured as an accumulator or an oil separator.