CN201747613U - Air exhaust and pressure reduction device of rotary compressor - Google Patents

Abstract

An exhaust and decompression device for a rotary compressor, comprising a compression mechanism part and a motor part arranged in an airtight casing, the compression mechanism part comprising a cylinder with a cylinder compression chamber in the center, a piston operating eccentrically in the cylinder compression chamber, The sliding plate whose tip is in contact with the outer circle of the piston, the eccentric crankshaft that drives the piston eccentrically, the main bearing and sub-bearing that support the eccentric crankshaft, and the exhaust muffler with the exhaust port installed on the main bearing, the motor part includes The stator assembly and the rotor assembly, the rotor assembly includes a cylindrical rotor core, and a decompression device is provided on the end of the rotor core facing the side of the exhaust muffler, the decompression device includes a gas passage provided therein, the Openings are respectively arranged at the center and the periphery of the end of the gas channel facing the rotor iron core, and the exhaust port of the exhaust muffler communicates with the gas channel. The utility model has the characteristics of low power consumption, high efficiency, stable compressor operation and wide application range.

Description

Discharge and pressure relief device for rotary compressors

technical field

The utility model relates to a rotary compressor, in particular to an exhaust and decompression device of the rotary compressor.

Background technique

In order to prevent global warming, it is imperative to improve the power consumption and efficiency of rotary compressors installed in air conditioners and refrigeration equipment. The exhaust muffler installed as a sound insulation measure for the rotary compressor increases the resistance of the high-pressure gas discharged from the compression chamber of the cylinder, and the power consumption of the compressor increases due to the increase in the exhaust pressure.

Utility model content

The purpose of this utility model is to provide a rotary compressor exhaust and decompression device with simple and reasonable structure, flexible operation, low power consumption, high efficiency, stable operation of the compressor, and a wide range of applications, so as to overcome the problems in the prior art. inadequacies.

A kind of exhaust decompression device of rotary compressor designed according to this purpose, comprises the compression mechanism part and the motor part that are arranged in the airtight housing, and the compression mechanism part includes the cylinder that is provided with the cylinder compression cavity in the center, works in the cylinder compression cavity. Pistons running eccentrically, slides whose tips are in contact with the outer circle of the pistons, eccentric crankshafts that drive the pistons eccentrically, main bearings and sub-bearings that support the eccentric crankshafts, and exhaust vents with exhaust ports provided on the main bearings The muffler, the motor part includes a stator assembly and a rotor assembly, the rotor assembly includes a cylindrical rotor core, and its structural feature is that a decompression device is provided on the end of the rotor core facing the side of the exhaust muffler, and the decompression device includes The gas passage arranged in it has openings in the center and outer periphery of the end of the gas passage facing the rotor iron core respectively, and the exhaust port of the exhaust muffler communicates with the gas passage.

The decompression device includes an end ring arranged on the end of the rotor core, the end ring is provided with a rotor disc, and more than one end ring groove is provided in the radial direction on the end ring, and the center of the rotor disc is provided with a The central hole, the inner wall of the end ring and the rotor disc together form a rotor cavity; the end ring groove set on the end ring is covered by the rotor disc, forming a gas passage from the rotor cavity to the outer circumference of the end ring; The muffler cylindrical part of the upper part of the muffler protrudes into or near the center hole.

The rotor disc is fixed on the end ring by rivets.

The decompression device includes an end ring arranged on the end of the rotor core, a disk is arranged on the end ring, and more than one through hole or slit is arranged radially on the side wall of the disk. There is a central hole in the center, and the inner wall of the end ring and the disc together form a cavity, forming a gas channel from the cavity to the outer circumference of the end ring; the muffler cylinder on the upper part of the exhaust muffler extends into or is close to the disc center hole.

The disc is fixed to the end ring by rivets.

The decompression device includes a disk arranged on the end of the rotor iron core, more than one through hole or slit is arranged radially on the side wall of the disk, a central hole is arranged in the center of the disk, and the rotor iron The end of the core and the disc together form a cavity, and form a gas channel from the cavity to the outer circumference of the end of the rotor core; the muffler cylinder at the top of the exhaust muffler extends into or is close to the disc Center hole.

The disc is fixed to the end of the rotor core by means of rivets.

The decompression device is arranged on the upper part of the eccentric crankshaft and is located in the range where the stator assembly is located.

The utility model constitutes a rotor cavity at the center of the end ring at the lower end of the rotor core, and sets several gas passages opening from the rotor cavity toward the outer periphery. The exhaust port of the exhaust muffler communicates with the rotor cavity, and passes Rotating, the pressure in the rotor chamber decreases, so the pressure in the exhaust muffler also decreases, which can reduce the power consumption of the compressor, improve work efficiency, and can also reduce the oil content of the exhaust gas, reduce the temperature of the motor coil, and improve compression. machine reliability.

The utility model is not only suitable for single-cylinder rotary compressors, but also suitable for double-cylinder rotary compressors. It has the advantages of simple and reasonable structure, flexible operation, low power consumption, high efficiency, stable compressor operation and wide application range. features.

Description of drawings

Fig. 1 is a longitudinal partial structural schematic diagram of Embodiment 1 of the utility model.

Fig. 2 is a partial enlarged structural schematic diagram of the compression mechanism part and the motor part.

Fig. 3 is a schematic diagram of a partially enlarged structure after the rotor core and the end ring are assembled.

FIG. 4 is a schematic bottom view of the structure of FIG. 3 .

Fig. 5 is a partial enlarged structural diagram of the assembled rotor core, end ring, and rotor disc.

FIG. 6 is a schematic bottom view of the structure of FIG. 5 .

Fig. 7 is a schematic diagram of a partially enlarged structure of a gas channel.

FIG. 8 is a curve diagram showing the variation of the rotation angle θ of the piston 28 and the internal pressure P of the cylinder compression chamber 24a.

FIG. 9 is a partially enlarged schematic diagram of the assembled rotor core and end ring in Embodiment 1. FIG.

FIG. 10 is a schematic bottom view of the structure of FIG. 9 .

In the figure: 1 is the rotary compressor, 2 is the airtight shell, 3 is the discharge pipe, 5 is the condenser, 6 is the evaporator, 7 is the expansion valve, 8 is the upper space of the shell, 13 is the liquid accumulator, 14 is Intake pipe, 15 is the exhaust hole, 16 is the eccentric crankshaft, 17 is the eccentric shaft, 18 is the exhaust muffler, 18a is the cylindrical part of the muffler, 19 is the exhaust muffler chamber, 20 is the rotor chamber, 21 is the compression mechanism part , 22 is the motor part, 23 is the stator assembly, 23a is the stator core, 23b is the motor winding, 24 is the cylinder, 24a is the compression chamber of the cylinder, 25 is the main bearing, 26 is the auxiliary bearing, 27 is the screw, 28 is the piston, 29 is a slide plate, 33 is lubricating oil, 40 is a rotor assembly, 40a is a rotor core, 40b is an end ring, 40c is a gas passage, 40e is an end ring groove, 41 is a rotor disc, 41a is a center hole, 42 is Rivet, 43 is a disc, C is a gap, and 44 is a disc.

Detailed ways

Below in conjunction with accompanying drawing and embodiment the utility model is described further.

Example 1

Referring to FIG. 1 , the rotary compressor 1 is composed of a compression mechanism part 21 installed in an airtight casing 2 and a motor part 22 arranged thereon. Lubricating oil 33 can be stored at the bottom of the airtight casing 2 .

The compression mechanism part 21 is composed of a cylinder 24, a piston 28 that operates eccentrically in the cylinder compression chamber 24a, a sliding plate 29 that reciprocates synchronously with the piston, an eccentric crankshaft 16 that drives the piston 28, and is connected to the eccentric crankshaft and fixed on the cylinder. The main bearing 25 on the 24 and the secondary bearing 26 constitute. An exhaust muffler 18 is provided above the main bearing 25 . The above components are assembled by upper and lower screws 27 to complete the compression mechanism part 21 . The outer circumference of the cylinder 24 of the compressed mechanism part 21 after assembly is fixed on the inner wall of the airtight casing 2 together with the motor part 22 .

Referring to FIG. 2 , it shows the internal structure of the rotary compressor 1 and details of the compression mechanism part 21 and the motor part 22 . The motor part 22 is composed of a stator assembly 23 and a rotor assembly 40, and the stator assembly 23 is composed of a stator core 23a and a motor winding 23b on the stator core.

Referring to FIGS. 3-4, details of the rotor core 40a are shown. The rotor core 40a is a cylinder with upper and lower end surfaces, and is composed of electromagnetic steel sheets (or iron cores) stacked to form a cylindrical part and an end ring 40b formed of aluminum material formed on the end surfaces. Several end ring grooves 40e are designed in the lower end ring 40b opposite to the compression mechanism part 21 in the first embodiment. These end ring grooves 40e are die-cast simultaneously with the end ring 40b, such as by die casting.

Referring to Figures 5-6, the rotor assembly 40 is shown. A rotor disc 41 is arranged on the end ring 40b of the rotor core 40a, and the center of the rotor disc 41 is provided with a central hole 41a. The rotor disc 41 is fixed on the end ring 40b by three rivets 42, and the rotor assembly 40 is completed. . In order to reduce the unbalance of the piston 28 , when a balance weight is added in the rotor assembly 40 , the balance weight is fixed together with the rotor disc 41 by rivets 42 .

Through the fixing of the rotor disc 41 , the rotor cavity 20 which is jointly surrounded by the inner wall of the end ring 40 b and the rotor disc 41 is formed. The end ring groove 40e provided on the end ring 40b is covered by the rotor disk 41, forming a gas passage 40c opening from the rotor chamber 20 to the outer periphery of the end ring 40b. The device formed by the rotor cavity 20 and the gas passage 40c is called a decompression device. The decompression device is arranged on the upper part of the eccentric crankshaft 16 and within the range where the stator assembly 23 is located. Correspondingly, the rotor assembly 40 is also fixed on the upper part of the eccentric crankshaft 16 and arranged within the range where the stator assembly 23 is located.

As shown in FIG. 1 , an air conditioning system equipped with a rotary compressor 1 is connected from a discharge pipe 3 in order of a condenser 5 , an expansion valve 7 , an evaporator 6 , an accumulator 13 , and a suction pipe 14 of the compressor. The gas sucked into the cylinder compression chamber 24 a from the suction pipe 14 becomes compressed high-pressure gas, and the high-pressure gas is discharged into the exhaust muffler chamber 19 through the exhaust hole 15 .

Subsequently, the gas discharged from the muffler cylindrical portion 18a through the rotor chamber 20 through the gas passage 40c towards the motor winding 23b mainly passes through the gap of the motor winding 23b to the housing upper space 8 above the motor portion 22 . The high-pressure gas collected in the housing upper space 8 is discharged from the exhaust pipe 3 to the condenser 5 . The pressure of the airtight casing in Embodiment 1 is equivalent to the pressure discharged from the cylinder compression chamber 24a, both of which are on the high pressure side.

Referring to FIG. 7 , it shows the connection of the gas circuit between the exhaust muffler 18 and the decompression device configured in the rotor assembly 40 . As previously described, the flow direction of the high-pressure gas discharged from the exhaust muffler chamber 19 is indicated by a dotted line. There is a sufficiently large gas passage between the muffler cylindrical portion 18 a and the outer periphery of the bearing portion of the main bearing 25 . By reducing the gap C formed with the center hole 41a, the gas located outside the exhaust muffler 18 can be prevented from leaking into the rotor cavity 20 . In Embodiment 1, the size of the gap C is set at 0.2 mm or less.

Since the rotor assembly 40 rotates, the peripheral speed of the gas channel 40c perforated on the outer circumference of the end ring 40b is faster than the inner circumference of the end ring 40b, so the pressure of the rotor cavity 20 is higher than the gas pressure of the sealed housing 2. Keep the pressure low. As a result, the pressure of the muffler chamber 19 communicating with the rotor chamber 20 will decrease, and the pressure of the exhaust gas discharged from the cylinder compression chamber 24a will decrease. The degree of the pressure drop is proportional to the outer diameter and rotation speed of the rotor assembly 40 and the gas density inside the airtight casing 2, and is also related to the design of the gas passage 40c.

If the drop pressure of the exhaust muffler chamber 19 is ΔP, the drop pressure ΔP is the pressure difference between the gas pressure of the airtight casing 2 and the exhaust muffler chamber 19 . However, ΔP=0 in a conventional rotary compressor that does not include a decompression device. In terms of the exhaust resistance of the exhaust muffler chamber, there is no pressure difference between Embodiment 1 and the conventional rotary compressor, so it is not included in ΔP.

Referring to Fig. 8, it shows the variation of the rotation angle θ of the piston 28 in the cylinder compression chamber 24a and the internal pressure P of the cylinder compression chamber 24a. The gas pressures of the conventional rotary compressor and the exhaust muffler chamber of Embodiment 1 are Pa and Pb respectively, and the exhaust pressure of the cylinder compression chamber 4a is equivalent to Pa and Pb. The pressure difference between Pa and Pb is ΔP. In FIG. 8 , the work reduction by the pressure difference ΔP is indicated by the hatched area, and the power consumption corresponding to the hatched area can be reduced in Embodiment 1 compared with the conventional rotary compressor.

Next, as a derivative effect of Embodiment 1, it has the function of improving the following two problems.

As shown in Example 1, in the rotary compressor whose shell pressure is the high pressure side, the temperature of the motor winding is the highest, so the gas discharged from the compression chamber of the cylinder with the lowest temperature must cool the motor winding. However, due to insufficient cooling, the operating range of the rotary compressor needs to be limited.

After lubricating the interior of the cylinder compression chamber, the high-pressure gas discharged from the cylinder compression chamber contains a large amount of lubricating oil. Due to this problem, the amount of oil discharged from the discharge pipe of the compressor will increase, and it is necessary to solve it.

In Embodiment 1, the high-pressure gas in the exhaust muffler cavity 19 can rush to the motor winding 23b, and in this way, the motor winding 23b made of many thin copper wires with higher temperature can pass through from above. During the passage, the lubricating oil mixed with the high-pressure gas separates and drops from the gas, and finally returns to the oil pool at the bottom of the airtight casing 2 . The high-pressure gas separated from the lubricating oil is discharged from the upper space 8 of the casing to the condenser 5 through the exhaust pipe 3 . As a result, in the rotary compressor 1, the amount of oil discharged can be significantly reduced.

At the same time, during the above process, the low-temperature high-pressure gas flowing into the upper space 8 of the casing can effectively directly cool the high-temperature motor winding 23b. As a result, the problem of reducing the temperature of the motor winding can be solved, the reliability of the motor can be improved, and the efficiency of the motor can be improved.

The above is the technical solution of opening the end ring groove 40e on the end ring 40b. This technical solution can also be replaced by the following technical solution, and the same technical effect as the above technical solution can be obtained.

The decompression device includes an end ring 40b arranged on the end of the rotor core 40a, a disk is arranged on the end ring 40b, and more than one through hole or slit is arranged radially on the side wall of the disk. The center of the disk is provided with a central hole, and the inner wall of the end ring 40b and the disk together form a cavity, forming a gas passage 40c from the cavity to the outer periphery of the end ring 40b; Portion 18a extends into or near the central hole of the disk. The disk may be secured to the end ring 40b by means of rivets 42 .

Example 2

Referring to Fig. 9-Fig. 10, it is an example of applying the technology disclosed by the present utility model in the DC variable frequency motor with no end ring in the rotor core 40a.

The decompression device includes a disc 44 arranged on the end of the rotor core 40a, the side wall of the disc 44 is provided with more than one through hole or slit in the radial direction, and the center of the disc 44 is provided with a central hole 41a , the end of the rotor core 40a and the disk 44 jointly form a cavity, and form a gas passage 40c from the cavity to the outer circumference of the end of the rotor core 40a; the muffler cylinder positioned at the top of the exhaust muffler 18 Portion 18a extends into or near the center hole of disc 44. The disk 44 is fixed to the end of the rotor core 40a by a rivet 42 . Of course, the depth of the disc 44 in this embodiment can be varied according to design requirements. The greater the depth of the disc 44, the greater the volume of the cavity.

See the first embodiment for the rest of the undescribed parts, and will not repeat them here.

Embodiment 1 and Embodiment 2 can be applied to a two-cylinder rotary compressor without substantially changing the structure. The general design of the two-cylinder rotary compressor is to make the gas discharged from the compression chambers of the two cylinders meet in the exhaust muffler equipped on the main bearing. In such a design, the exhaust muffler can increase the exhaust resistance, and the power consumption will deteriorate. However, this problem can be solved by the devices disclosed in Embodiment 1 and Embodiment 2.

Claims (8)

1. A discharge and decompression device of a rotary compressor, comprising a compression mechanism part (21) and a motor part (22) arranged in the airtight housing (2), the compression mechanism part comprising a central cylinder compression chamber (24a ), the piston (28) that operates eccentrically in the cylinder compression chamber (24a), the sliding plate (29) whose tip end is in contact with the outer circle of the piston (28), and the eccentrically driven piston (28) The eccentric crankshaft (16), the main bearing (25) and auxiliary bearing (26) supporting the eccentric crankshaft (16), and the exhaust muffler (18) with an exhaust port arranged on the main bearing (25), the motor part (22) includes a stator assembly (23) and a rotor assembly (40), and the rotor assembly (40) includes a cylindrical rotor core (40a), which is characterized in that the rotor core (40a) faces the exhaust muffler (18)- A decompression device is provided on the end of the side, and the decompression device includes a gas channel (40c) disposed therein, and the gas channel (40c) is respectively provided with Opening, the exhaust port of the exhaust muffler (18) communicates with the gas channel (40c). 2. The exhaust decompression device of a rotary compressor according to claim 1, characterized in that said decompression device comprises an end ring (40b) arranged on the end of the rotor core (40a), the end ring ( 40b) is provided with a rotor disc (41), and the end ring (40b) is provided with more than one end ring groove (40e) in the radial direction, and the center of the rotor disc (41) is provided with a central hole (41a). The inner wall of the ring (40b) and the rotor disc (41) together form the rotor cavity (20); the end ring groove (40e) provided on the end ring (40b) is covered by the rotor disc (41), forming a (20) The gas channel (40c) of the peripheral opening of the end ring (40b); the muffler cylindrical part (18a) located on the upper part of the exhaust muffler (18) extends into or near the central hole (41a). 3. The exhaust and decompression device of a rotary compressor according to claim 2, characterized in that the rotor disc (41) is fixed on the end ring (40b) by rivets (42). 4. The exhaust decompression device of a rotary compressor according to claim 1, characterized in that said decompression device comprises an end ring (40b) arranged on the end of the rotor core (40a), the end ring ( 40b) is provided with a disk, the side wall of the disk is provided with more than one through hole or slit radially, the center of the disk is provided with a central hole, and the inner wall of the end ring (40b) and the disk jointly form a The cavity forms a gas channel (40c) that is opened from the outer periphery of the cavity opposite end ring (40b); the muffler cylindrical part (18a) located on the upper part of the exhaust muffler (18) extends into or near the center hole of the disc. 5. The exhaust and decompression device for a rotary compressor according to claim 4, characterized in that the disc is fixed on the end ring (40b) by a rivet (42). 6. The exhaust decompression device of a rotary compressor according to claim 1, characterized in that said decompression device comprises a disk (44) arranged on the end of the rotor core (40a), the disk ( 44) on the side wall radially provided with more than one through hole or slit, the center of the disk (44) is provided with a central hole (41a), the end of the rotor core (40a) and the disk (44) Together they form a cavity, and form a gas channel (40c) from the cavity to the outer periphery of the end of the rotor core (40a); Or close to the central hole (41a) of the disc (44). 7. The exhaust and decompression device for a rotary compressor according to claim 6, characterized in that the disc (44) is fixed on the end of the rotor core (40a) by a rivet (42). 8. The exhaust decompression device of a rotary compressor according to any one of claims 1 to 7, characterized in that the decompression device is arranged on the upper part of the eccentric crankshaft (16) and is located in the range where the stator assembly (23) is located Inside.

Images