KR20050062216A - Gear type compressor - Google Patents

Abstract

The present invention relates to a gear-type compressor that can improve the performance coefficient of the refrigeration system.

To this end, the present invention and the drive unit; A gear type compression unit installed at an upper side of the driving unit to receive a driving force of the driving unit to compress the refrigerant introduced from the evaporator; It is provided on the upper side of the gear-type compression unit, the gear-type expansion unit for discharging the refrigerant is discharged from the gear-type compression unit and re-absorbed via the condenser: provides a gear-type compressor comprising a.

Description

Gear type compressor

The present invention relates to a compressor, and more particularly to a compressor of the gear type.

In general, a compressor is a machine that increases the pressure of a working fluid by receiving power from a power generator such as an electric motor or a turbine and applying compression work to air, a refrigerant, or other special gas. It is widely used in general household appliances such as the field to the plant industry.

On the other hand, such compressors are classified into positive displacement compressors and dynamic compressors or turbo compressors according to the compression method.

Among them, a widely used industrial compressor is a volumetric compressor, which has a compression method of increasing pressure through volume reduction. The volumetric compressor is further classified into a reciprocating compressor and a rotary compressor.

The reciprocating compressor compresses the working fluid by a piston reciprocating linearly inside the cylinder, and has a merit of obtaining a high compression efficiency with a relatively simple mechanical element. On the other hand, the size and weight of the machine is increased, the reciprocating compressor has a limitation in the rotational speed due to the inertia of the piston, there is a disadvantage that significant vibration occurs due to the inertia force.

The rotary compressor compresses the working fluid by a roller revolving with the eccentricity inside the cylinder, and can obtain a high compression efficiency at a low speed compared to the reciprocating compressor.

However, in order to change the flow rate at a constant rotational speed, the rotary compressor needs to discharge extra air or throttle the intake air, and to provide a stabilizer in order to increase the discharge pressure caused by the extra air. It becomes difficult.

In addition, if the gap between the parts is not very uniform, compressed gas may leak and may not be able to exert its performance. Thus, highly precise machining is required. In addition, the bearing load is easily damaged due to the acting load due to the rapid pressure change.

That is, the rotary compressor and the reciprocating compressor have different characteristics and advantages and disadvantages, respectively.

On the other hand, a refrigeration cycle is a thermodynamic cycle, when the purpose of extracting heat to the cold reservoir by applying work (working) is called a refrigeration cycle (refrigeration cycle), the system forming the refrigeration cycle is a refrigeration cycle It is called a system and it is mainly used in refrigerators and air conditioners.

In addition, referring to FIG. 1, the refrigerating system extracts heat from a compressor 30 that compresses the refrigerant at a high temperature and high pressure, and extracts heat from the refrigerant compressed by the compressor 30 to the outside to make the refrigerant into a liquid state. A condenser 50, an expansion valve 40 for adiabatic expansion of the refrigerant flowing from the condenser 50, and a pressure drop, and the refrigerant passing through the expansion valve 40 to a low pressure gas while absorbing external heat. Consisting of an evaporator 60.

For reference, FIG. 2 is a graph showing the pH diagram of the refrigeration system of FIG. 1, which receives the work (Wc) from the outside to compress the refrigerant in the compressor 30 (1 → 4), and compresses in the compressor 30. The refrigerant is released through the condenser 50 to the heat of the refrigerant to the outside (2 → 3).

The refrigerant passing through the condenser 50 is adiabaticly expanded while passing through the expansion device 20 (3 → 4), and the refrigerant passing through the expansion device receives external heat while passing through the evaporator 60. (4 → 1), the refrigerant passing through the evaporator 60 flows back into the compressor (30).

The coefficient of performance (COP) of this refrigeration system is defined as the compressor work (Wc) for the amount of heat Q _H absorbed by the low temperature section, that is, the evaporator 60.

Therefore, in order to construct an efficient refrigeration system, it is necessary to configure an efficient compressor with an appropriate refrigerant selection.

In recent years, the necessity of alternative refrigerants such as CO2 is very important as the problem of freon gas, which is a refrigerant, destroys the ozone layer.In this case, even when using an alternative refrigerant, there is no fear of leakage during compression, and mechanical reliability is secured. A compressor is needed.

It is an object of the present invention to provide a compressor having a new structure that can improve the performance coefficient of a refrigeration system different from the existing compressor structure.

In order to achieve the above object, the present invention and the drive unit; A gear type compression unit installed at an upper side of the driving unit to receive a driving force of the driving unit to compress the refrigerant introduced from the evaporator; It is provided on the upper side of the gear-type compression unit, the gear-type expansion unit for discharging the refrigerant is discharged from the gear-type compression unit and then re-absorbed through the condenser provides a gear-type compressor comprising a.

At this time, the drive unit is characterized in that the motor is made of a stator and a rotor is installed in the center thereof to rotate when the power is applied to the stator.

And, the gear-type compression unit, the main bearing is fixed to the upper side of the motor; An annular compression cylinder connected to an upper portion of the main bearing; An external gear rotatably positioned in the compression cylinder inner space; An internal gear installed inside the external gear to compress the refrigerant while being engaged with the external gear by receiving the driving force of the motor; Characterized in that it comprises a compression plate that is connected to the upper compression cylinder.

In addition, the external gear is characterized in that it is formed to have more teeth grooves than the number of teeth of the inner gear is coupled to the rotating shaft of the motor.

In addition, one side of the compression plate is characterized in that the sub-compression suction pipe (sub compression suction pipe) is connected to the compression plate to send the refrigerant to the outer gear inner space.

And, the other side of the compression plate is characterized in that the compression discharge pipe (compression discharge pipe) for sending the compressed refrigerant to the condenser.

In addition, the compression plate is characterized in that the suction port and the discharge port are formed at a predetermined position, respectively.

In addition, the gear-type expansion unit, the expansion plate is fixed to the upper side of the motor; An annular expansion cylinder connected to the upper portion of the expansion plate; An external gear rotatably positioned in the expansion cylinder inner space; An internal gear installed inside the external gear to expand the refrigerant while being engaged with the external gear by receiving the driving force of the motor; It characterized in that it comprises a sub-bearing is installed in contact with the upper expansion cylinder.

In addition, one side of the sub-bearing is characterized in that an expansion suction pipe (expander suction pipe) is installed so that the refrigerant passing through the condenser is introduced into the expansion cylinder.

In addition, the other side of the sub-bearing is characterized in that an expander discharge pipe (expander discharge pipe) for sending the expanded refrigerant to the evaporator.

In addition, the sub-bearing is characterized in that the suction port and the discharge port is formed at a predetermined position, respectively.

In addition, the outer size of the gear-type expansion portion is characterized in that formed in a smaller size than the outer size of the gear-type compression portion.

Hereinafter, an embodiment of the present invention will be described in detail with reference to the accompanying drawings, FIGS. 3 to 6.

3 is a cross-sectional view showing the configuration of a gear type compressor according to the present invention.

4A is a cross-sectional view taken along the line I-I of FIG. 3, and FIG. 4B is a cross-sectional view taken along the line II-II of FIG. 3, and is a cross-sectional view showing the geometry of the inner and outer gears of the compression part and the expansion part.

On the other hand, Figure 5 is a block diagram showing the configuration of a refrigeration system to which the gear type compressor of the present invention is applied.

In the gear type compressor of the present invention, a casing 1 having a predetermined space therein, a driving part 2 installed inside the casing 1, and a driving force of the driving part 2 are received from the evaporator 6; And a gear type expansion unit 4 for compressing the introduced refrigerant, and a gear type expansion unit 4 for discharging the refrigerant sucked out through the condenser 5 after being discharged from the gear type compression unit 3. It is composed.

At this time, the driving unit 2 is a stator 200 mounted on the inner wall of the casing 1 and a rotor 210 installed at a central portion thereof to rotate when power is applied to the stator 200 through the power terminal 110. It consists of a motor.

In addition, the gear type compression unit 3 (that is, the compression unit), the main bearing 300 is fixed to the motor upper side of the casing 1 and the annular annularly installed in the upper portion of the main bearing 300 Compression cylinder of the 310, the external gear 320 is rotatably located in the compression cylinder 310 inner space, and receives the driving force of the motor is engaged with the external gear 320 while rotating the external to compress the refrigerant It includes an inner gear 330 is installed inside the gear 320, and the compression plate 340 is installed in contact with the upper portion of the compression cylinder (310).

At this time, a suction pipe 100 (suction pipe) for introducing a refrigerant into the casing (1) is installed on one side of the upper casing (1).

In addition, a base plate 120 for installing a compressor is provided below the casing 1.

In addition, a compression unit connected to the compression plate 340 on one side of the compression plate 340 to send the refrigerant introduced into the casing 1 to the inner space of the external gear 320 through the compression cylinder 310. A suction pipe 350 is provided, and a compression discharge pipe 360 is installed at the other side of the compression plate 340 to send the compressed refrigerant to the condenser 5. .

On the other hand, the gear type expansion unit 4 (that is, the expansion unit), the expansion plate 400 is installed on the compression plate 340 of the gear type compression unit 3, and the expansion plate 400 Annular expansion cylinder 410 is installed in contact with, the external gear 420 rotatably positioned in the inner space of the expansion cylinder 410 and, while receiving the driving force of the motor is engaged with the outer gear 420 It includes an inner gear 430 is installed inside the outer gear 420 to expand the refrigerant, and a sub-bearing 440 is connected to the upper portion of the expansion cylinder 410.

In addition, an expansion suction pipe 450 is installed at one side of the sub-bearing 440 to allow the refrigerant passing through the condenser 5 to flow into the expansion cylinder 410.

And, the other side of the sub-bearing 440 is provided with an expansion discharge pipe 460 (expander discharge pipe) for sending the expanded refrigerant to the evaporator (6).

In addition, the suction plate 340a and the discharge port 340b are formed at predetermined positions in the compression plate 340, and the suction port 440a and the discharge port 440b are disposed at the predetermined positions in the sub-bearing 440. Each is formed.

On the other hand, the outer size of the inflation portion 4 is formed to a size smaller than the outer size of the compression portion (3).

That is, the outer size of the sub-bearing 440, the expansion cylinder 410 and the expansion plate 400 is formed in a smaller size than the outer size of the main bearing 300, the compression cylinder 310 and the compression plate 340 desirable.

Accordingly, the operation of connecting the compression unit sub suction pipe 350 and the compression unit discharge pipe 360 to the compression plate 340 constituting the gear type compression unit 3 can be easily performed.

On the other hand, the reason that the outer size of the gear-type expansion portion 4 may be formed in a smaller size than the outer size of the gear-type compression portion 3, the gear size of the gear-type expansion portion 4 is a gear-type compression This is because it is smaller than the gear size of the section 3.

This is due to the specific volume difference between the refrigerant flowing into the suction port 340a in the gear type compression unit 3 and the refrigerant flowing into the suction port 440a in the expansion unit 4 and expanding the expansion unit 4. Since the specific volume of the refrigerant flowing into the suction port 440a of the c) is small, in order for the mass flow of the expansion process and the compression process to achieve the same mass flow rate, the administrative volume of the expansion process must be smaller than the administrative volume of the compression process. This is because the gear size of the gear type expansion part 4 should be smaller than the gear size of the gear type compression part 3.

However, the difference in gear size does not have a direct relationship with the difference in external size of the compression cylinder 310 and the expansion cylinder 410.

Hereinafter, the compressor of the present invention configured as described above will be described with reference to FIGS. 3 to 6.

First, referring to FIGS. 3 and 5, the refrigerant is compressed in the gear type compression unit 3 according to the operation of the driving unit 2, and the refrigerant compressed in the gear type compression unit 3 then passes through the flow path. Therefore, it is introduced into the condenser 5, and the heat is discharged to the outside while passing through the condenser (5).

The refrigerant passing through the condenser 5 flows into the gear type expansion part 4 of the compressor of the present invention through a flow path, and the refrigerant introduced into the gear type expansion part 4 expands in the process of passing through the expansion part. do.

Subsequently, the refrigerant passing through the gear type expansion part 4 flows into the evaporator 6, and the refrigerant absorbs heat from the outside while passing through the evaporator 6.

Then, the refrigerant passing through the evaporator 6 flows back into the gear type compression unit 3, and this series of flows is repeated to form a refrigeration cycle.

The compression and expansion operations performed by the present invention compressor during the process of forming the refrigeration cycle as described above will be described in more detail with reference to FIGS. 3 and 5.

First, when power is applied to a motor mounted on the inner wall of the casing 1 and the rotor 210 rotates by electromagnetic interaction with the stator 200, the suction pipe 100 installed at the upper end of the casing 1 (suction) The refrigerant flows into the casing 1 through the pipe.

Then, the refrigerant introduced into the casing 1 is sent to the inner space of the external gear 320 through a sub compression suction pipe 350 connected to the compression plate 340.

At this time, the refrigerant passing through the compression portion suction pipe 350 is introduced into the outer gear 320 inner space through the suction port 340a of the compression plate 340 in communication with the inner space of the outer gear 320.

The refrigerant sent to the inner space of the outer gear 320 is gradually compressed according to the rotation of the inner gear 330 axially coupled to the motor shaft 220, and then passes through the discharge port 340a formed in the compression plate 340. It is discharged through the compression part discharge pipe 360 connected to the discharge port 340a and sent to the condenser 5.

Here, the area of the discharge port 340a in the gear type compression unit 3 is smaller than that of the suction port 340a.

Meanwhile, the refrigerant that has undergone the heat exchange process in the condenser 5 is re-introduced into the gear type expansion part 4 of the compressor of the present invention.

That is, the refrigerant having undergone the heat exchange in the condenser 5 passes through the expansion part suction pipe 450 connected to one side of the sub bearing 440, and then the external gear 420 through the suction port 440 a of the sub bearing 440. The refrigerant flowing into the inner space and sent to the inner space of the outer gear 420 is gradually expanded according to the rotation of the inner gear 430 axially coupled to the motor shaft 220 and then discharged to the other side of the sub bearing 440. It is discharged through the expansion part discharge pipe 460 connected to the port 440b is sent to the evaporator (6).

Here, the area of the discharge port 440b in the gear type expansion part 4 is larger than that of the suction port 440a.

On the other hand, the gear-type compression unit 3 and the gear-type expansion unit 4 is preferably all installed in one casing (1), as in the above-described embodiment, each separately installed in a separate casing (1) May be

In addition, the drive unit 2 may also be installed outside the casing 1, and of course, as the drive unit 2, an electric motor that generates rotational force by electric energy is generally used. Any ramen is possible.

On the other hand, Figure 4a is a cross-sectional view taken along the line I-I of Figure 3, illustrating the geometry of the inner gear 330 and the outer gear 320 forming the gear type compression section (3).

At this time, the outer gear 320 is formed to have more teeth grooves 320a than the number of teeth 330a of the inner gear 330 that is coupled to the motor shaft 220 and rotates of the inner gear 330. The center of rotation of the center and the outer gear 320 is installed eccentrically.

Typically, the number of teeth 330a of the inner gear 330 is smaller than the number of teeth grooves 320a of the outer gear 320, and the shape of the teeth 330a preferably forms a cycloid curve.

4B is a cross-sectional view taken along the line II-II of FIG. 3 to illustrate the geometric shapes of the inner gear 430 and the outer gear 420 constituting the gear type expansion part 4. The structure of the inner gear 430 and the outer gear 420 of the gear type expansion part 4 is the same as that of the inner gear 330 and the outer gear 320 of the gear type compression part 3, and only the size thereof It's different.

6 is a graph comparing the torque change generated by the compressor of the present invention with the torque generated by the conventional compressor, wherein the vertical axis is a torque ratio obtained by dividing each torque value T by an average value Tm of torques generated during rotation. The horizontal axis represents the rotation angle.

Referring to this, it can be seen that the amount of torque change generated when the refrigerant is compressed by the compressor according to the structure of the present invention is significantly smaller than that of the compression device having another structure.

In particular, in the gear type compressor of the present invention, vibration and noise are reduced by maintaining a balance of torque as the external gears 320 and 420 rotate together with the inner gears 330 and 430 during refrigerant compression and expansion.

In addition, in the gear type compressor of the present invention, the teeth 330a and 430a formed in the inner gears 330 and 430 and the teeth grooves 320a and 420a of the outer gears 320 and 420 are contacted with each other. Therefore, there is an effect that the force transmitted from the inner gear to the outer gear is dispersed without being concentrated in one place.

In addition, the gear type compressor of the present invention at the point where the teeth 330a, 430a formed in the inner gears 330, 430 and the teeth grooves 320a, 420a of the outer gears 320, 420 are engaged. Speed difference, i.e., the relative speed is small.

On the other hand, the gear type compressor of the present invention can be used as a refrigerant carbon dioxide refrigerant.

Carbon dioxide has a long service life as a refrigerant, is not toxic and nonflammable. In addition, the price is low, the source is abundant, there is no need to recover, it can be dissolved well with lubricating oil, and the amount of cooling per unit volume is five times higher than that of CFC series R-22. Compression ratio also has the advantage of being smaller.

Therefore, when using the gear type compressor of the present invention it is possible to fully utilize the above advantages by using carbon dioxide as a refrigerant.

As described above, the present invention can provide a gear-type compressor, it is possible to improve the performance coefficient of the refrigeration system.

On the other hand, according to the present invention, it is possible to replace the refrigerant used in the compressor with carbon dioxide, there is an advantage that the environmentally friendly compressor can be implemented.

That is, carbon dioxide has a long service life as a refrigerant, not only toxic but also nonflammable. In addition, the price is low, the source is abundant, there is no need to recover, it can be dissolved well with lubricating oil, and the amount of cooling per unit volume is five times higher than that of CFC series R-22. Compression ratio also has the advantage of being smaller.

In addition, the gear-type compressor of the present invention has the advantage of reducing the vibration and noise when operating the compressor due to the balance of the force and torque of the internal gear and the external gear.

1 is a conceptual diagram showing the configuration of a typical refrigeration system

2 is a graph showing a P-h diagram of the refrigeration system of FIG.

3 is a cross-sectional view showing the configuration of a gear type compressor according to the present invention.

FIG. 4A is a cross-sectional view taken along the line I-I of FIG. 3, showing a geometric shape of the inner gear and the outer gear of the compression unit.

FIG. 4B is a cross-sectional view taken along the line II-II of FIG. 3 and shows the geometrical shape of the inner gear and the outer gear of the inflation portion.

5 is a configuration diagram of a refrigeration system to which the gear type compressor of the present invention is applied;

Figure 6 is a graph comparing the torque change generated in the compressor of the present invention with the torque generated in the conventional compressor

* Description of the symbols for the main parts of the drawings *

1: Casing 100: suction pipe

110: power terminal 120: base plate

2: drive unit 200: stator

210: rotor 220: rotating shaft

3: Compression part 300: Main bearing

300a: suction port 310: compression cylinder

320: External gear 320a: Teeth groove

330: Internal gear 330a: Teeth

340: compression plate 340a: discharge port

350: compressed part suction pipe 360: compressed part discharge pipe

4: expansion part 400: expansion plate

410: expansion cylinder 420: external gear

420a: Teeth groove 430: Internal gear

430a: Teeth 440: Sub Bearing

440a: suction port 440b: discharge port

450: expansion part suction pipe 460: expansion part discharge pipe

5: condenser 6: evaporator

Claims (13)

A drive unit; A gear type compression unit installed at an upper side of the driving unit to receive a driving force of the driving unit to compress the refrigerant introduced from the evaporator; And a gear type expansion unit installed at an upper side of the gear type compression unit to expand the refrigerant that is discharged from the gear type compression unit and then resorbed through the condenser. The method of claim 1, The driving unit, Gear type compressor characterized in that the motor is made of a stator and a rotor installed in the center of the rotor to rotate when the power is applied to the stator. The method of claim 1, The gear type compression unit, A main bearing fixed to the upper side of the driving unit; An annular compression cylinder connected to an upper portion of the main bearing; An external gear rotatably positioned in the compression cylinder inner space; An internal gear installed inside the external gear to compress the refrigerant while being engaged with the external gear by receiving the driving force of the driving unit; Compression plate which is installed in contact with the compression cylinder upper portion: a gear type compressor, characterized in that comprises a. The method of claim 3, wherein And a sub-compression suction pipe connected to one side of the compression plate to connect the refrigerant to the inner space of the external gear. The method of claim 3, wherein The other side of the compression plate is a gear-type compressor, characterized in that the compression discharge pipe (compression discharge pipe) for sending the compressed refrigerant to the condenser. The method of claim 3, wherein And a suction port and a discharge port are formed at predetermined positions on the compression plate. The method of claim 1, The gear type expansion unit, An expansion plate fixed to an upper side of the driving unit; An annular expansion cylinder connected to the upper portion of the expansion plate; An external gear rotatably positioned in the expansion cylinder inner space; An inner gear installed inside the outer gear to expand the refrigerant while being engaged with the external gear by receiving the driving force of the driving unit; The sub-bearing is installed in contact with the upper portion of the expansion cylinder: a gear type compressor comprising a. The method of claim 7, wherein And a expander suction pipe installed at one side of the sub-bearing to allow refrigerant passing through the condenser to flow into the expansion cylinder. The method of claim 7, wherein The other side of the sub-bearing gear type compressor characterized in that an expander discharge pipe (expander discharge pipe) for sending the expanded refrigerant to the evaporator is installed. The method of claim 7, wherein And a suction port and a discharge port are formed at predetermined positions in the sub bearing. The method according to any one of claims 3 to 7, The outer gear is a gear type compressor, characterized in that it is formed to have more teeth grooves than the number of teeth of the inner gear is coupled to the rotating shaft of the drive unit. The method of claim 1, The outer size of the gear type expansion portion is a gear type compressor, characterized in that formed in a smaller size than the outer size of the gear type compression portion. The method of claim 1, Gear type compressor, characterized in that the casing surrounding both the drive unit and gear type compression unit and gear type expansion unit is provided.