KR20210002281A - A Laundry Treatment Apparatus - Google Patents

Abstract

The present invention relates to a compressor using R-290, which is a flammable refrigerant, a heat pump using the compressor, and a clothes treatment apparatus using the compressor. Since R-290, a flammable refrigerant, should be used according to environmental regulations, redesign of the compressor, evaporator, condenser, and expansion valve constituting the heat pump is required for optimization of the heat pump, and accordingly, the present invention relates to a clothes treatment apparatus reflecting the redesign.

Description

A Laundry Treatment Apparatus}

The present invention relates to a clothing treatment apparatus using a flammable refrigerant.

A general clothing treatment device uses a heater or a heat pump to dry laundry. In particular, a clothing treatment apparatus using a heat pump dehumidifies and cools moist air using an evaporator and a condenser, and then heats it again to supply the dried high-temperature air to the clothing. Compared to the method of using a heater, high-temperature heat can be generated with a small amount of work, and thus, it is widely used in recent years because it is excellent in terms of energy efficiency.

A refrigerant is essential to realize the refrigeration cycle of such a heat pump. The refrigerant is a working fluid that is easy to evaporate in the refrigeration cycle. It takes the heat of the low temperature part and transports it to the high temperature part.

Natural refrigerant of refrigerant, 1st generation CFC (Chlorofluorocarbon, chlorofluorocarbon), 2nd generation HCFC (Hydro chlorofluorocarbon), 3rd generation HFC (hydrofluorocarbon), 4th generation HFO (Hydrofluoroolefin), etc. It can be classified as Among them, CFC and HCFC refrigerants classified as Freon gas are known as major substances for ozone depletion, and are regulated by the Montreal Protocol.

HFC series does not destroy the ozone layer, but is a global warming material. A representative refrigerant corresponding to this is R-134a, which is used in automobiles and household electronics. This refrigerant was classified as one of the six major global warming substances in the Kyoto Protocol, but it could be used because it was not forced. However, as it was regulated as a regulated substance for ozone depletion by the Montreal Protocol in 1987, it is expected to be banned in developed countries by 2020 and before 2030 in developing countries. In addition, as HFC-series refrigerants were included in European fluorinated greenhouse gas (F-gas) regulations in 2006, HFO-series refrigerants with low GWP are emerging as the next-generation refrigerants.

Global warming potential (GWP) represents the degree to which other greenhouse gases contribute to global warming based on the impact of carbon dioxide on global warming. That is, it refers to the value obtained by dividing the amount of solar energy absorption of 1 kg of individual greenhouse gas by the amount of solar energy absorption of 1 kg of carbon dioxide. The warming effect per unit mass is indexed. For example, considering carbon dioxide as 1, methane is 21, nitrous oxide is 310, hydrogen fluoride is 1,300, and sulfur hexafluoride is 23,900.

In Europe, in particular, if the GWP exceeds 150, the sale of commercial closed refrigeration units in Europe will be prohibited from 2020.Central refrigeration units for commercial use with a GWP exceeding 150 and exceeding 40 kW will also be banned from 2022 Market sales are prohibited.

To cope with this, a heat pump using R-290 and a clothes treatment device using the same are being developed. As prior literature, there are European Patent Publication No. EP2871432A1 or European Patent Publication No. EP2985466A1, which relates to a rotary compressor and a heat pump used in small household appliances. All of the prior literature uses a rotary compressor having a height-to-radius ratio of 1.2 to 1.4 of the rollers inside the rotary compressor. In addition, it is disclosed that a polyester-based synthetic oil called POE is used as a refrigerant oil according to the change in the number of fins of the evaporator and condenser according to the use of R-290 and the use of the R-290 refrigerant.

However, the prior literature relates to a rotary compressor using a vane and a heat pump using the same, and relates to the use of a single cylinder having a height-to-radius ratio of 1.2 to 1.4 of a roller inside the rotary compressor. That is, the refrigerant is compressed and used using only one roller, one vane, and one cylinder. As described above, since the ratio of the height to the radius of the roller is 1 or more, the friction loss with the cylinder is large, and the amount of refrigerant flowing between the roller and the cylinder increases. In addition, since the eccentric mass is one, the vibration increases, and by using one cylinder, the axial weight applied to the eccentric roller or the eccentric portion increases, and eventually, the moment of inertia is large, so that more bending moment and shear force are applied to the drive shaft.

In addition, the refrigerant oil used in the prior literature is a POE (polyester)-based synthetic oil. POE-based synthetic oil has a high cleaning effect, so it can emulsify by washing all kinds of lubricants, anti-rust coatings, oxides generated during welding, and flowing along the refrigeration cycle, which can cause failure. In addition, there is a problem of very absorbing moisture when exposed to moisture.

To solve this problem, first, we intend to develop a rotary compressor that uses the R-290 refrigerant and has the same refrigeration performance as the existing R-134a. Second, we intend to develop a twin compressor whose height-to-radius ratio of the inner roller is less than 1. Third, it is intended to reduce the friction loss between the roller and the cylinder and the leakage loss of the refrigerant that escapes through the gap between the vane and the roller during compression. Fourth, it is intended to reduce vibration and noise by using a twin compressor having a symmetrical eccentric portion, and fifth, to reduce the axial load and the moment of inertia applied to the drive shaft. Through this, we intend to develop an evaporator, a condenser, and a capillary tube to have the same or superior refrigeration performance as the existing R-134a according to the compression of the R-290 refrigerant. Seventh, it is intended to use oil suitable for such refrigeration performance. Sixth, we intend to develop a laundry treatment device using this.

In the case of using a flammable refrigerant, the design of the heat pump must be changed for the same performance as the existing R-134a.

First, a change in compressor design is required. Comparing the new flammable refrigerant R-290 and the existing refrigerant R-134a, the difference between condensation pressure and evaporation pressure is also R- in ASHRAE 37 (The American Society of Heating, Refrigerating and Air-Conditioning Engineers) evaluation conditions. 134a is 1355 kPa, R-290 is 1666 kPa, which is larger than R-134a, and the specific volume of the refrigerant (R-134a is 0.000845 ㎥/kg, R-290 is 0.00208 ㎥/kg). In addition, for the same refrigeration capacity, the R-290 can reduce the stroke volume by 25%. Considering this, the stroke volume of the compressor can be reduced. In addition, in order to reduce noise and vibration, friction loss and leakage loss in the compressor, it is recommended that the ratio of the height to radius of the eccentric roller used in the compressor be less than 1, so that a twin compressor is used.

Second, it is necessary to change the evaporator pipe size. If the same diameter and length of the pipe is used as the volume flow rate is given, it is supersaturated at the evaporator outlet, which causes an unreasonable effect on the compressor. Reducing the diameter increases the speed of the refrigerant.

Third, the length or diameter of the condenser pipe should be shortened to prevent the condenser from becoming subcooled at the outlet.

Fourth, due to the refrigerant change, it is necessary to use oil for compressor refrigerant, so we intend to change from POE, a synthetic oil used due to the polarity of R-134a, to a 5GSD type, which is a mineral oil.

Fifth, to reduce the copper loss of the compressor motor used in the compressor and expand the effective slot area, a two-stage stator core having a step at the upper end is used.

Specifically, the compressor case, a circular first cylinder located inside the compressor case to provide a first chamber, a circular second cylinder located inside the compressor case to provide a second chamber, the first cylinder and the first cylinder 2 A diaphragm located between the cylinders and separating the first and second chambers, a first eccentric roller located in the first chamber and rotatable in contact with the inner circumferential surface of the first cylinder, and located in the second chamber. It includes a second eccentric roller rotatable in contact with the inner circumferential surface of the second cylinder, and a drive shaft penetrating the first cylinder, the second cylinder and the diaphragm, one end is fixed to the first cylinder, and the other end is the first eccentric A first vane that contacts a roller and is installed to enable a reciprocating motion when the first eccentric roller rotates, one end is fixed to the second cylinder, the other end contacts the second eccentric roller, and the second eccentric roller A second vane that is installed to enable a reciprocating motion during rotation, a first inlet port for introducing a refrigerant into the first chamber, a second inlet port for introducing a refrigerant into the second chamber, and passing through the first bearing A compressor discharge unit including a first discharge port for discharging the refrigerant in the first chamber and a second discharge port for discharging the refrigerant in the second chamber through the second bearing, and the first eccentric roller and the first Two eccentric rollers are to provide a compressor, characterized in that the height-to-radius ratio (Height-to-radius ratio) is 0.75 or more and 0.8 or less, respectively.

More specifically, the stroke volume of the compressor is 8 cc/revolution or more and 10 cc/revolution or less, the effective areas of the first and second discharge ports are 25 mm2 or more and 26 mm2 or less, respectively, and the radius of the drive shaft is 5.5 mm Is 7.5 mm or less and the thickness of the first discharge port and the second discharge port is 1.5 mm or more and 2.5 mm or less, respectively.

In addition, in the compressor, eccentricities of the first eccentric roller and the second eccentric roller are located in opposite directions with respect to the drive shaft, so that the first discharge port and the second discharge port alternate when the drive shaft rotates once. As a result, the compressed refrigerant may be discharged.

In addition, the compressor may use R-290 as a refrigerant and 5GSD type as an oil.

In addition, further comprising a power generating unit for rotating the drive shaft, the power generating unit includes a compressor motor that generates rotational force by electromagnetic force, the compressor motor includes a rotor coupled to the drive shaft and a stator on which a coil is wound. To provide a compressor.

In addition, using the oil to lubricate the drive shaft, the power generation unit, the first vane, the second vane, the first eccentric roller, the second eccentric roller, the first bearing and the second bearing. It is to provide a compressor further comprising an oil passage portion for supplying oil to the hazard.

In addition, a first bearing that is coupled to one surface of the first cylinder located in a direction away from the diaphragm to rotatably support the drive shaft, and is coupled to one surface of the second cylinder located in a direction away from the diaphragm to rotate the drive shaft And a second bearing capable of supporting the second bearing, wherein the first discharge port passes through the first bearing to discharge the refrigerant in the first chamber, and the second discharge port passes through the second bearing A first discharge valve for discharging the refrigerant in the two chambers, the compressor discharge unit being located in the first bearing and discharging only when the pressure of the refrigerant discharged through the first discharge port is equal to or higher than a preset pressure; A second discharge valve positioned on the second bearing and configured to discharge only when the pressure of the refrigerant discharged through the second discharge port is equal to or higher than a preset pressure; It is to provide a compressor characterized in that it further comprises.

When configuring a heat pump using the compressor, the evaporator included in the heat pump includes a plurality of evaporator heat exchange fins for heat exchange, an evaporator pipe passing through the plurality of evaporator heat sinks and reciprocating a plurality of times, and the evaporator heat sink is air Hydrophilic coating may be applied to prevent moisture condensed in the evaporator from adhering to the heat dissipation fin.

In addition, the condenser included in the heat pump includes a plurality of condenser radiating fins for heat exchange and a condenser pipe passing through the plurality of condenser radiating fins and reciprocating a plurality of times, and the diameter of the condenser pipe is designed to be smaller than the diameter of the evaporator pipe. I can.

In addition, the refrigerant pipe included in the heat pump may include a suction pipe connecting the evaporator and the compressor; A discharge pipe connecting the compressor and the condenser; And an expansion unit connecting the evaporator and the compressor, wherein the expansion unit includes a capillary tube for lowering the pressure of the refrigerant, and the length of the capillary tube may be 1250mm or more and 1350mm or less.

In addition, it is to provide a laundry treatment apparatus having a drying function using the heat pump.

First, it is intended to provide an optimized compressor according to the use of R-290 refrigerant. This can reduce friction loss and flow loss between the roller and the cylinder.

Second, it is possible to prevent supersaturation at the outlet while increasing heat exchange efficiency by changing the diameter of the evaporator pipe and changing the heat transfer area.

Third, by changing the diameter of the condenser pipe and changing the heat transfer area, it is possible to prevent subcooling at the outlet while increasing heat exchange efficiency.

Fourth, by using 5GSD mineral oil as the oil, it is less sensitive to moisture exposure and can reduce cost compared to synthetic oil.

Fifth, it is possible to increase the efficiency of the compressor motor by using a two-stage stator core.

Sixth, the durability of the product can be increased by designing a heat pump using this.

1 shows a laundry treatment apparatus according to an embodiment of the present invention.
2 shows a front supporter, a filter and a front duct.
3 shows a rear porter and a rear duct.
4 shows an embodiment of the coupling relationship and arrangement between the mechanical parts of the base unit.
Figure 5 schematically shows the air circulation flow of the laundry treatment apparatus of the present invention.
6 shows another embodiment of the coupling relationship and arrangement between the mechanical parts of the base unit.
7 shows the evaporator, the condenser and the compressor, and the refrigerant pipe.
8 shows a compressor which is an embodiment of the present invention.
Fig. 9 is an enlarged view of Fig. 8A.
Fig. 10 shows one end of the compressor cylinder.
Figure 11 (a) is a stator of the conventional compressor motor and (b) shows the stator of the compressor motor provided in the laundry treatment apparatus of the present invention. (c) is a stator core of a conventional compressor motor, and (d) is a stator core of a compressor motor provided in the laundry treatment apparatus of the present invention.
12 is a cross-sectional view of another embodiment of a compressor used in the laundry treatment apparatus of the present invention.
13 is a cross-sectional view of another embodiment of a compressor used in the laundry treatment apparatus of the present invention.
14 is an embodiment of a condenser used in the laundry treatment apparatus of the present invention.
15 is an embodiment of an evaporator used in the laundry treatment apparatus of the present invention.
Figure 16 (a) is a diagram showing the connection of the refrigerant pipe and the expansion unit, (b) is an expansion unit (c) is a discharge pipe (d) is an embodiment of a suction pipe.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings. On the other hand, the configuration or control method of the device to be described below is for explaining the embodiment of the present invention, not to limit the scope of the present invention, and reference numerals used identically throughout the specification are the same components. Show them.

Specific terms used in the present specification are merely for convenience of description and are not used as limitations of the illustrated embodiments. For example, expressions representing relative or absolute arrangements such as "in which direction", "along any direction", "parallel", "orthogonal", "center", "concentric" or "coaxial" are strictly such It is assumed that not only the arrangement is indicated, but also the state in which the displacement is relatively displaced with tolerances or angles and distances at a degree to which the same function is obtained.

For example, expressions indicating that things are in the same state, such as ``same'', ``is the same'', and ``homogeneous'', not only indicate exactly the same state, but also a tolerance or a difference in the degree to which the same function is obtained. It also shows the state.

For example, an expression indicating a shape such as a square shape or a cylindrical shape not only indicates a shape such as a square shape or a cylindrical shape in a geometrical strict sense, but also includes an uneven portion or a chamfer within the range in which the same effect is obtained. It is assumed that the shape is also shown.

On the other hand, the expression "to prepare", "have", "have", "include", or "have" one component is not an exclusive expression excluding the presence of another component.

In addition, in the present specification, the same or similar reference numbers are assigned to the same or similar configurations even in different embodiments, and redundant descriptions thereof will be omitted.

Structures applied to one embodiment may be equally applied to another embodiment, as long as different embodiments do not contradict structurally and functionally.

Singular expressions include plural expressions unless the context clearly indicates otherwise.

In describing the embodiments disclosed in the present specification, when it is determined that a detailed description of related known technologies may obscure the subject matter of the embodiments disclosed herein, the detailed description thereof will be omitted.

The accompanying drawings are only for making it easier to understand the embodiments disclosed in the present specification, and the technical idea disclosed in the present specification is not limited by the accompanying drawings, and all changes and equivalents included in the spirit and scope of the present invention It should be understood to include water or substitutes.

The present invention relates to a laundry treatment apparatus using a flammable refrigerant such as R-290.

As described above, the fourth generation HFO refrigerant is (i) non-toxic and stable. (ii) It shows an appropriate solubility in mineral oil, which is a refrigerant oil. (iii) There is no risk of destruction of the ozone layer and the global warming index (GWP) is very low. On the other hand, 4th generation HFO refrigerants such as R-290 are flammable or flammable. Therefore, in the case of leakage, if the concentration of the flammable refrigerant exceeds 1.8%, there is a risk of ignition or explosion during use. (ii) When used in home appliances, the maximum charging amount of flammable refrigerant is limited to 150 g by international regulations on the maximum charging amount. Therefore, in order to achieve the same performance as the existing R-134a, a redesign of the heat pump used in the existing laundry treatment system is required.

In other words, R-290 has similar critical pressure and critical temperature compared to R-134a, but the difference between evaporation pressure and condensation pressure is 1.2 times larger, and the specific volume of refrigerant (R-134a is 0.000845 ㎥/kg, R- 290 is larger than 0.00208 m3/kg). In addition, considering the latent heat of evaporation, for the same refrigeration capacity, the stroke volume of the R-290 can be reduced by 25%. In addition, when the latent heat of evaporation is high, the amount of refrigerant at least increases the refrigeration efficiency. From this point of view, R-290 can be seen as a good alternative refrigerant for R-134a.

However, a redesign of the refrigerant pipe including the compressor, evaporator, condenser, and expansion unit of the heat pump is required in consideration of this. However, several safety designs to detect leakage and prevent explosions are also required at the same time.

1 is a schematic diagram showing the appearance of an embodiment of a laundry treatment apparatus 100 that performs a drying function using a heat pump using a flammable refrigerant, for example R-290. Referring to FIG. 1, the laundry treatment apparatus includes a cabinet 101 that is a main body of the laundry treatment apparatus in a substantially rectangular parallelepiped shape, and a circular inlet 106 is provided in the front surface 103 of the cabinet. A control panel 104 that controls various functions of the dryer and displays an operating state may be provided on the front side 103.

The front surface 103 of the cabinet may be provided with a door 108 that is rotatably coupled to the cabinet 101 to open and close the inlet 106. Whether the door 108 is opened or closed may use a non-contact detection sensor using a magnet in place of detection by a conventional electric contact method. This is to prevent the risk of explosion when a flammable refrigerant such as R-290 is used, or if a flammable refrigerant leaks. That is, in the conventional electrical contact method, when the electrical contact is pressed, spark may occur, and the phosphite refrigerant may explode by the spark.

In order to prevent this in advance, a magnetic portion 1082 provided on one side of a door that can be operated in a non-contact manner without using an electrical contact and provided at a position corresponding to the magnetic portion 1082 by being located on the front surface 103 of the cabinet. It may be provided with a sensing unit (1083).

The sensing unit 1083 may include a reed switch for sensing the magnetic force (or magnetic force) of the magnetic unit 1082. Therefore, as the door 108 approaches the inlet 106, the reed switch is turned on by the magnetic force of the magnetic unit 1082 even if the magnetic unit 1082 does not contact the sensing unit 1083. ) So that the door can be detected.

The inside of the cabinet 101 includes a cylindrical drum 110 in communication with the inlet 106 to accommodate laundry. In the lower portion of the drum 110, a base portion in which mechanical parts including a duct 120 for circulating air in the drum 110 and a heat pump 140 for reheating the air in the duct after dehumidifying cooling are located ( 130) may be provided. The base unit 130 may provide a floor surface of the cabinet 101 as well as a space in which mechanical parts to perform various functions of the laundry treatment apparatus 100 may be installed. This will be described later with reference to FIGS. 4 to 7.

In addition, the door 108 may include a light transmitting part. Accordingly, even when the door 108 is closed, the inside of the drum 110 may be visually exposed through the light transmitting part.

The drum 110 has a cylindrical shape and may be provided in a shape in which both the front side and the rear side are opened. However, this is only an exemplary embodiment, and the front side may be opened and the rear side may be closed. This may vary depending on how the drum 110 operates.

For example, a drum drive shaft (not shown) for rotating the drum at the rear of the drum is provided, and the drum drive shaft (not shown) is directly coupled to a drum motor to rotate the drum 110 by the drum motor. I can. In addition, a drum drive shaft for driving the drum at the rear of the drum is coupled to the drum, and a drum drive shaft other than the drum can be rotated using a drive motor and a pulley, and a belt connecting the pulley and the drum drive shaft. In this case, since the drum 110 does not need a follower for supporting and rotating the drum at the rear side of the drum, the rear side of the drum may not need to be opened. Accordingly, the rear side of the drum is not opened and is closed, and a drum drive shaft for rotating the drum can be coupled to the rear surface of the drum.

Hereinafter, using an embodiment in which the front and rear sides of the drum 110 are opened and rotatable by a front supporter 104 and a rear supporter 105 for supporting rotation of the drum, the clothing I will describe the processing device. The front supporter 104 and the rear supporter 105 are disposed at the front and rear sides of the drum 110, respectively, and may support the drum 110 in a rotatable manner.

2, the front supporter 104 has an opening 1042 corresponding to the front opening of the drum 110 for inputting the object to be treated, and the lower circumferential portion is in communication with the front duct 1210. An outlet 1041 is formed. The front duct 1210 extends downward to the base portion and is combined with the filter installation portion 1242 to form an inlet duct. 2 shows that the front duct 1210 is configured to include the front duct connector 1212 and the filter guide 1211, but unlike this, it may be formed of only the front duct connector 1212.

Therefore, the air dried on the object to be treated in the drum 1030 passes through the inlet duct where the front duct 1210 and the filter installation unit 1242 (refer to FIG. 4) are combined, and a blowing fan (not shown) located at the blowing fan installation unit 127 Poetry). After that, the dried heated air passes through the evaporator 142 and the condenser 143, and then passes through the rear duct 230 and circulates back to the drum.

The filter guide 1211 is mounted on the front supporter 104 and inserted into the outlet 1041. The filter guide 1211 may be mounted on the circumference of the front supporter 104. The filter 124 is detachably coupled to the inside of the filter guide 1211 and is configured to filter lint in the air discharged through the front opening of the drum 110. In addition, the filter 124 may include a plurality of filters. That is, unlike FIG. 2, the inner filter may be inserted into the outer filter, and the outer filter may be inserted into the filter guide 1211 to pass through the outlet 1041. In addition, the number of holes in the mesh network per unit area of the outer filter and the inner filter may be configured differently. In one embodiment, the mesh network of the inner filter may be formed to be denser than that of the outer filter. The filter 124 may be inserted along the filter guide 1211 and installed inside the front duct connector 1212. In addition, the base unit 130 includes a filter installation unit 1242 having a size corresponding to the front duct connector 1212, and may be combined with the front duct connector 1212 to form an induct that is an air circulation channel. In contrast, when the filter 124 is formed of a front duct connector 1212 without a filter guide 1211 in the front duct 1212, a filter is installed in the filter installation part 1242 so that the outlet ( 1041) can filter the air containing foreign matter.

3 is a conceptual diagram showing a structure behind the drum 110 shown in FIG. 1. Referring to FIG. 3, a rear drum support ring 1053 corresponding to a rear opening (not shown) of the drum 110 may be formed to protrude on a front surface of the rear supporter 105 facing the drum 110. The rear drum support ring 1053 may be inserted into the rear opening of the drum 110 to rotatably support the drum. However, this is only one embodiment for rotating the drum. It is also possible to rotate in a different manner from that of supporting and rotating the body of the drum using the supporter 105. For example, a drum drive shaft for rotating the drum at the rear of the drum is provided, and the drum drive shaft is connected to a drum motor 180 (refer to FIG. 4) to thereby control the drum 110 by the drum motor 180. Can be rotated directly. In addition, the drum drive shaft for driving the drum at the rear of the drum is coupled to the drum, and the drum drive shaft other than the drum may be rotated using a drive motor and a pulley, and a belt connecting the pulley and the drum drive shaft.

Hereinafter, as shown in FIG. 3, an embodiment including a supporter will be described. A rear drum support ring 1053 corresponding to a rear opening (not shown) of the drum 110 may be protruded on the front surface of the rear supporter 105. The rear drum support ring 1053 may be inserted into a rear opening (not shown) to rotatably support the drum 110.

At least two drum rollers 115 are rotatably mounted on the supporter 105. The drum roller 115 rotatably supports the drum 110 under the drum 110.

In order to prevent air from leaking into the gap between the rear opening (not shown) of the drum 110 and the rear drum support ring 1053, a sealing pad (not shown) may be disposed to cover the connection portion. The sealing pad (not shown) is formed to cover and surround the rear opening (not shown) of the drum 110 and the rear drum support ring 1053.

In the follower 105, an inlet 1051 corresponding to the rear opening (not shown) of the drum 110 is formed. The inlet 1051 may be formed at a position eccentric to one side with respect to a vertical reference line passing through the center of the supporter 105. In addition, the inlet 1051 may be formed above a horizontal reference line passing through the center of the follower 105.

Alternatively, the inlet 1051 may be formed in all areas corresponding to the rear opening (not shown). The rear ductor 105 may be equipped with an inlet 1051 and a rear duct connector 1231 for discharging the air passing through the condenser and a rear duct 230 for connecting the inlet 1051. If the blowing fan is after the condenser, the ventilation fan outlet 1272 and the rear duct connector 1231 through which air is discharged are connected, and then the rear duct connector 1231 and the inlet 1051 are connected. The connecting rear duct 230 may be mounted.

A rear protrusion 1052 protruding rearward may be formed in a portion of the rear supporter 105 in which the rear duct 230 is not disposed. Accordingly, the front of the rear porter 105 may have a shape that is relatively recessed toward the rear. Therefore, the inner space of the drum 1030 can be further secured.

The rear duct 230 is formed to extend upward and may be configured to guide the dried heated air through the heat exchanger to the inlet 1051 of the rear porter 105.

4 is a water supply unit for cleaning the heat pump 140 including the duct 120, the compressor 200, the drum motor 180 and the evaporator 142 located in the base unit 130, which is the lower part of the drum 110 ( 160) is a picture of the arrangement.

A duct 120 that serves to circulate air is positioned in the base unit 130. If the duct is subdivided, it can be classified as follows. The second flow path centered on the evaporator 142 and the condenser 143, the first flow path defined by the front duct 1210 and the blower fan installation part 127, the rear duct connector 1231 and the rear duct 230 The flow path defined by can be divided into a third flow path. Accordingly, air inside the drum 110 may be discharged through the first passage, dehumidification and heat exchange may be performed in the second passage, and may be introduced into the drum 110 through the third passage.

Among them, the second flow path uses the bottom surface of the base unit 130 as the bottom surface of the second flow path, and covers the evaporator 142 and the condenser 143 to form the ceiling of the second flow path. And it may be formed using the cover side (not shown). Unlike this, the second flow path may be formed as a single member to allow air to flow.

The first flow path forms a path through which air discharged from the outlet 1041 flows in, and may extend toward the bottom surface of the base unit 130. The second flow path may extend in a straight line toward the rear of one side of the base unit 130. The third flow path may extend upward from one side of the base portion 130 to the inlet 1051.

The second flow path extends in a straight line from the base portion 130, thereby preventing a decrease in heat exchange efficiency and reducing flow resistance.

Some of the components constituting the heat pump 140 are installed inside the duct 120, particularly on the second flow path, and the heat pump 140 includes a compressor 200, an evaporator 142, a condenser 143, and an expansion unit. It may include a refrigerant pipe 146 including 145.

The duct 120 passes through the drum 110 in the cabinet 101 and becomes a path for air to dry the object to be dried. In particular, the duct 120 is formed in a duct shape inside the cabinet 101 from the front to the rear of the cabinet 101.

The evaporator 121 and the condenser 124 are installed in the duct 120, and the expander and the compressor are disposed on the base 130 of the cabinet 101 outside the circulation passage. Here, the evaporator 121 is mounted closer to the first flow path in the duct 120 than the condenser 124. Accordingly, the air introduced from the filter installation unit 1242 in terms of air flow passes through the duct 120 and sequentially passes through the evaporator 121 and the condenser 124, and cooling (condensation) and reheating are performed accordingly. do.

In the drum 110 rotated in the cabinet 101 by the drum motor 180, heated air is discharged through the rear duct 230 to dry laundry inside the drum. The air used for drying contains moisture evaporated from the laundry and becomes humid air, and the lint filter installation part 112 and the duct 120 communicated with the outlet 1041 in front of the drum 110 near the door 108 side. ).

Meanwhile, the heat pump 140 refers to a device that cools and heats air circulating through a circulation passage by heat exchange with a refrigerant. In the heat pump 140, the evaporator 142, the compressor 200, the condenser 143, and the expansion unit 145 are sequentially connected by a refrigerant pipe 146 through which a refrigerant flows. Among the configurations of the heat pump 140, the evaporator 142 and the condenser 143 are configured to directly heat exchange with circulating air.

The refrigerant circulating through the heat pump 140 absorbs heat from the hot and humid air exiting the drum from the evaporator 142 and evaporates. Accordingly, the circulating air is cooled, and the moisture contained in the air is condensed and falls to the bottom of the duct-shaped circulation channel by gravity.

On the other hand, the refrigerant circulating through the pipe of the heat pump 140 is evaporated in the evaporator 142, compressed at high temperature and high pressure in the compressor 200, and then transferred to the cooled circulation air in the condenser 143. It is condensed. Accordingly, the circulating air is heated to become hot dry air and is discharged back to the drum 110 by the rear duct 230.

In addition, the cooled refrigerant expands through the expansion unit 145 and becomes a state in which heat can be absorbed by the evaporator 142 again. The expansion part 145 may be provided as an expansion valve, or may be provided as a capillary tube using an orifice phenomenon. In addition, a filter dryer 1465 may be provided to filter out foreign substances in the refrigerant.

Meanwhile, the condensed water generated while condensing by the evaporator 142 may fall to the bottom surface where the evaporator and the condenser are located, and may be primarily collected in a condensate collection unit (not shown). The condensed water collected in this way may be introduced into the condensed water storage unit 161 located adjacent to the compressor 200.

The condensed water which is introduced into the condensed water storage unit 161 and stored and stored may be supplied to a control valve (not shown) installed above the cover plate 140 by the water pump 165. Condensed water supplied through the water supply pipe 166 connected between the water pump 165 and the control valve (not shown) is provided with a plurality of water supply ports 1611, 1612, 1613 and a drain port 168 provided in the control valve (not shown). ) Can be discharged. The condensed water may be supplied to the injection pipe 167 through a plurality of water supply ports 1611, 1612, 1613.

The injection pipe 170 has a pipe shape with a central portion bent, and a discharge port (not shown) of the injection pipe 170 penetrates through the cover plate 128, and the bottom surface of the cover plate 128, that is, of the base portion 130 It is arranged to protrude toward the bottom surface. In addition, a discharge port (not shown) of the injection pipe 170 is provided on the bottom of the cover plate 140 to spray condensed water into the evaporator 142. It is not necessary to spray all areas of the evaporator, and can only be sprayed in areas where foreign matter contained in the air discharged from the drum may accumulate.

A drum motor 180 for driving the drum 110 may also be mounted on the base unit 130. The position of the drum motor 180 may vary depending on a method of driving the drum 110. In the case of direct coupling with the drum driving shaft of the drum 110 at the rear of the drum, the drum motor 180 must be located at the rear of the drum, and thus cannot be located at the base unit 130. However, in the case of rotating the drum 110 using a belt, a belt (not shown) for transmitting the driving force of the drum motor 180 and the drum motor 180 to the drum 11 transmits the rotational force to any part of the drum. Depending on the delivery, the position at the bottom of the drum can change. For example, when rotating the cylindrical body of the drum, it may be located at the lower center of the drum as shown. However, when the drum drive shaft is rotated, it may be located at the rear and lower portions of the drum. Hereinafter, the drum motor 180, the blowing fan, and the box fan 2001 for cooling the compressor 200 will be described later with reference to FIG. 7.

5 illustrates air circulation and refrigerant circulation in the laundry treatment apparatus according to an embodiment of the present invention. In one embodiment of the present invention, it is shown that the blowing fan is located in the first flow path part of the duct 120, but in some cases, the blowing fan installation part 127 is located after passing through the condenser 143 so that the rear duct 230 It may be provided to discharge air.

6 is after passing through the evaporator 142 and the condenser 143 to supply air to the rear duct 230 by the blowing fan installation part 127 and the blowing fan 1273 (not shown) located inside the blowing fan installation part. It is an installed embodiment.

7 shows the evaporator 142 and the condenser 143 by removing the cover plate 128 from the duct 120. With reference to FIG. 7, the drum motor 180, the blowing fan 1273, and the box fan 2001 will be described.

The drum motor 180 is for generating a driving force for rotation of the drum 110, and a belt (not shown) for transmitting the driving force of the drum motor 180 to the drum 100 is connected to the drum motor 180. I can. The belt may be disposed to surround the outer periphery of the drum 110.

In addition, a pulley 181 and a spring (not shown) may be used to adjust the tension applied to the belt. Pulley 181 may be configured to apply a certain tension (Tension) to the belt. The pulley 1811 may be configured to be rotatable on a drum motor mounting unit (not shown) located on the base unit 130 on which the drum motor is mounted or a bracket (not shown) mounted on the drum motor mounting unit (not shown).

In order to adjust the tension of the belt, the drum motor 180 may be configured to be rotated around one axis within a certain angle range and then returned to the initial position by the elastic force of the spring. To this end, the drum motor 180 is configured to be rotatable about one axis in the drum motor mounting portion, and the spring may be connected to the drum motor mounting portion and the drum motor 180, respectively.

Meanwhile, a blower fan 1273 may be mounted on the shaft of the drum motor 180. In an embodiment of the present invention, a belt is connected to a shaft provided on one side of the drum motor 180, and a blowing fan 1273 may be mounted on a shaft provided on the other side of the drum motor 180.

Accordingly, shafts provided on both sides of the drum motor 180 are rotated in the same direction and at the same speed. When two shafts are provided in one drum motor 180, there may be many advantages in terms of improving power consumption of the clothing treatment apparatus 100. Basically, compared to the case in which the drum motor 180 for rotating the drum 110 and the drum motor for rotating the blowing fan 1273 are respectively provided, power consumption may be reduced by half.

The time point at which the blowing fan 1273 is required to rotate is the same as the time point at which the drum 110 rotates. This is because, while the drum 110 rotates, high-temperature dry air is supplied to the drum 110, and hot and humid air may be discharged from the drum 110. Accordingly, a state in which rotation of any one of the drum 110 and the blowing fan 1273 is unnecessary does not occur.

A box fan 2001 may be installed adjacent to the compressor 200. The box fan 2001 may be configured to generate wind toward the compressor 200 or to suck and blow air around the compressor 200. The temperature of the compressor 200 may be lowered by the box fan 2001, and as a result, compression efficiency may be improved. In an embodiment of the present invention, it is shown that the box fan 2001 is located at the rear of the compressor 200 and is located close to the rear of the cabinet.

A cabinet discharge hole (not shown) for exchanging air outside the cabinet and air inside the cabinet may be formed in the cabinet 101 in which the box fan 2001 is located. Preferably, a cabinet discharge hole (not shown) may be formed at the rear of the cabinet in which the box fan 2001 is located. However, since the cabinet 101 is not a closed structure, a gap generated during coupling forms a cabinet discharge hole, and air inside the cabinet and air outside the cabinet may be exchanged using the gap.

The box fan 2001 may be provided for other purposes. That is, in the case of using a flammable refrigerant such as R-290, a safety measure is required to prevent explosion. This is because when the flammable refrigerant leaks and is collected inside the cabinet due to a density heavier than air, it may explode due to an electrical spark. In order to prevent such an explosion, it is necessary to reduce the concentration of the flammable refrigerant to less than the explosive concentration by providing a flow of air where the flammable refrigerant is expected to collect, or to discharge the flammable refrigerant to the outside of the cabinet.

The place where leakage is expected is near the compressor 200 with many vibrations and many joints. Accordingly, the leaked refrigerant may collect in the vicinity of the compressor 200 except for the duct 120 in the base unit 130. At this time, if the fan 2001 is used, the air inside the cabinet 101 is circulated, and the concentration of the leaked refrigerant can be diluted. In addition, it can be discharged to the outside through the cabinet discharge hole, and the concentration of the leaked refrigerant can be lowered by introducing outside air into the inside. Accordingly, the fan 2001 may not only cool the compressor, but also induce air circulation or exchange of air when the flammable refrigerant leaks, thereby preventing explosion through dilution of the leaked refrigerant.

8 to 13 relate to a compressor 200 of a heat pump provided in a clothes treatment apparatus using a flammable refrigerant according to an embodiment of the present invention.

The compressor 200 of the heat pump according to an embodiment of the present invention is a rotary compressor, and a compressor case 203 having a cylindrical shape and a first cap 201 and a second cap 202 blocking both ends of the case are installed. It forms a closed interior space. In addition, it may include a compressor bottom fixing portion 290 that couples the compressor case 203 to the base unit 130. In contrast, the first cap 201 and the second cap 202 may be provided in a hemispherical shape, or may be welded to the case and provided in an integrated form.

It may include a compressor motor 210 for generating power located inside the compressor case 203 and a compression unit 220 for compressing a refrigerant using power. The compressor motor 210 may receive power through the compressor case 203 or the terminal 218 located in the first cap 201 or the second cap 202. In FIG. 8, the compressor motor 210 is located above the compressor, and the compression unit 220 is located below the compressor, but their positions may be changed as necessary.

The compressor motor 210 includes a stator 217 of the compressor motor fixed to the compressor case 203, a rotor 216 of the compressor motor rotatably supported inside the stator 217 of the compressor motor, and the compressor motor. It includes a drive shaft 214 pressed into the rotor 216. The rotor 216 of the compressor motor rotates by electromagnetic force, and the drive shaft 214 transmits the rotational force of the rotor 216 of the compressor motor to the compression unit 220.

The refrigerant inlet 281 for sucking the refrigerant may be installed on one side of the compressor case 203 and may be connected to an accumulator 280 that separates the gas phase and the liquid phase of the refrigerant. In addition, a compressor discharge pipe 2281 through which the compressed refrigerant is discharged may be installed in the first cap 101. In addition, the second cap 202 may be filled with a certain amount of oil (or refrigerant oil) to lubricate and cool the frictional member.

At this time, the end of the drive shaft 214 is immersed in oil. Therefore, when oil is supplied along the oil passage part (not shown) located inside the drive shaft 214, the oil may be dissolved in the refrigerant and circulated together. Therefore, strictly, the refrigerant circulated in the heat pump is a mixed fluid of oil and refrigerant.

The conventional compression unit 220 in the form of a single cylinder may be composed of a roller positioned inside a cylinder, a cylinder fixed to the case, and upper and lower bearings respectively installed at the upper and lower portions of the cylinder. The cylinder must have an internal volume of a predetermined size and must be designed to have sufficient strength to withstand the pressure of the compressed fluid. The cylinder also houses an eccentric roller portion formed on the drive shaft within the inner volume. The eccentric roller part is a combination of an eccentric cam and roller. Accordingly, it has a center spaced apart from the rotation center of the drive shaft by a predetermined distance.

In addition, a groove extending to a predetermined depth from the inner circumferential surface of the cylinder may be formed. A vane is installed in the groove, and the vane is in contact with the eccentric roller to divide an internal volume into a 1-1 chamber and a 1-2 chamber. The first and second chambers do not have a fixed volume, but change according to the motion of the eccentric roller, and may provide a space for compressing an internal refrigerant.

However, in the case of flammable refrigerants, for example, R-290 has a specific volume in a liquid state of 0.000845 ㎥/kg for R-134a and 0.00208 ㎥/kg for R-290, compared to R-134a, which is about 2.5 times the specific volume of R-290. Big. In general, about 500 g of R-134a is charged in the laundry treatment device, but the R-290 can only be charged to less than 150 g by regulation. Therefore, the overall volume considering the amount to be charged is rather reduced in R-290. Actually, an error may occur in the amount of filling in the production process of the laundry treatment apparatus, and it may preferably be charged to 145 g or less. The difference between condensing pressure and evaporation pressure is 1355 kPa in ASHRAE 37 (The American Society of Heating, Refrigerating and Air-Conditioning Engineers) evaluation conditions, and R-290 is 1666 kPa, which is greater than R-134a. Therefore, considering the difference between condensing pressure and evaporation pressure, for similar refrigeration capacity, R-290 can reduce the stroke volume by 25%. Therefore, the approximate stroke volume is 8 cc or more and 10 cc or less per one revolution of the compressor. If it exceeds 10cc, a heat generation problem of the compressor occurs, and if it exceeds 8cc, the amount of refrigerant is small and sufficient heat exchange is impossible. Therefore, for optimal performance while replacing the existing R-134a with a flammable refrigerant, the stroke volume of the compressor should be 8cc/rev or more and 10cc/rev or less.

In order to compress such flammable refrigerants, in order to use the conventional single cylinder type, the number of rollers that actually compress the refrigerant must be designed in consideration of the stroke volume. In order to install on the base 130 of the laundry treatment apparatus, the radius of the compressor roller cannot be increased, so in general, the ratio of the height to the radius of the eccentric roller in a single cylinder (hr:rr, see Fig. 10) is 1.2 or more and 1.6 or less. Use. However, when the ratio of the height to the radius of the roller is large for compression, the friction loss inside the cylinder in contact with the outer circumferential surface of the roller increases. In addition, the refrigerant in both chambers separated by the vane may flow out through the gap between the vane and the roller, or between the vane and the cylinder, and between the vane and the bearing. This is called leakage loss. Therefore, when the height is increased, a larger gap is generated, so that the leakage loss of the refrigerant increases. In particular, in a rotary compressor using a vane, this loss is relatively large for other compressors. In order to reduce this, it may be desirable to use the case where the ratio of the height to the radius of the roller is 1 µm.

Therefore, taking into account the need for a lot of compression work per unit mass due to the large specific volume of flammable refrigerant, friction loss between the eccentric roller and the cylinder, fluid loss during compression, and the space where the compressor is installed, the roller Although the ratio of the height to radius of is less than 1, the compression work per unit mass is reduced, and the compressed refrigerant is divided and compressed simultaneously in order to reduce frictional loss and fluid loss.

For this purpose, referring to FIG. 8, the compression unit 220 of the compressor 200 used in the laundry treatment apparatus according to an embodiment of the present invention is largely two cylinders 2211 and 2212 fixed to the compressor case 203. , It may include two eccentric roller parts 2231 and 2232 positioned inside each cylinder, and a partition wall 2223 for preventing refrigerant from being mixed by separating the two cylinders. The first cylinder 2211 may be combined with the first bearing 2251 on the opposite surface of the surface meeting the partition wall, and the second cylinder 2212 may be combined with the second bearing 2252 on the opposite surface of the surface meeting the partition wall. have.

Each of the cylinders 2211 and 2212 has chambers 2291 and 2292 having a predetermined volume and must be designed to have sufficient strength to withstand the pressure of the compressed fluid. Further, the cylinders 2211 and 2212 may accommodate a first eccentric roller 2231 and a second eccentric roller 2232 formed on the drive shaft inside the chambers 2291 and 2292. The first eccentric roller 2231 and the second eccentric roller 2232 are a kind of eccentric cam and have a center (L2, see FIG. 10) spaced apart from the rotation center of the drive shaft (L1, see FIG. 10) by a predetermined distance. The first eccentric roller 2231 and the second eccentric roller 2232 may be a combination of an eccentric portion and a roller, but may be a single member.

Further, each of the cylinders 2211 and 2212 may have cylinder grooves 2211a and 2212a (refer to FIG. 9) extending from the inner circumferential surface to a predetermined depth. The first cylinder groove (2211a) and the second cylinder groove (2212a) are respectively provided with a first vane (2241) and a second vane (2242), the first vane (2241) and the second vane (2242), respectively In contact with the first eccentric roller 2231 and the second eccentric roller 2232, the internal volume can be divided into two, respectively. Referring to Fig. 10, the first chamber 2291 includes a first vane 2241 and a first eccentric roller. It can be divided into a 1-1 chamber 2291a and a 1-2 chamber 291b, respectively by 2231. The chambers 2291a and 2291b divided into two do not have a fixed volume, but 1 It changes according to the motion of the eccentric roller, and it is possible to provide a space for compressing by introducing a refrigerant inside.

The refrigerant supplied to the first chamber 2291 and the second chamber 2292 is a first inlet port (2814a) and a second inlet port (2814b) passing through the first cylinder (2211) and the second cylinder (2212), respectively. Is supplied through. When the refrigerant that has passed through the accumulator 280 is supplied through the refrigerant inlet 281, the first cylinder 2211 and the first cylinder 2211 and through the first inlet port 2814a and the second inlet port 2814b branched in a Y-shape, respectively. It is supplied into the second cylinder 2212.

8 shows that one inlet port is branched into the first inlet port 2814a and the second inlet port 2814b inside the compressor, but this corresponds to an embodiment. The first inlet port 2814a and the second inlet port 2814b may not be inclined, and as in FIG. 12, the refrigerant from the accumulator 280 starts from the first inlet portion 2811 and the second inlet portion ( 2812) and can also be introduced.

Referring to FIG. 9, the operating principle of the rotary compressor will be described. Fig. 9 is a schematic cross-sectional view of the first cylinder of Fig. 8; The first cylinder 2211 may include a first cylinder groove 2211a for elastically fixing one end of the first vane 2241. The other end of the first vane 2241 is always in contact with the first eccentric roller 2231. This is due to the elastic force of the elastic member 2233. Accordingly, the first chamber 2291 is divided into two chambers by the first vanes 2241 and is divided into a 1-1 chamber 2291a and a 1-2 chamber 291b, respectively.

The driving shaft 214 may include a first oil passage 261 that supplies oil for lubrication. The drive shaft 214 may be coupled with an eccentric first eccentric roller 2231. When the drive shaft 214 rotates, the first eccentric roller 2231 performs a rolling motion along the inner circumferential surface of the first cylinder 2211. Accordingly, the volumes of the 1-1 chamber 2291a and the 1-2 chamber 291b are continuously changed. In one chamber, the refrigerant is introduced, and in the other chamber, the refrigerant is compressed. When the refrigerant is compressed to a predetermined pressure or higher, the first discharge valve 2271a is opened to discharge the compressed refrigerant through the discharge port 2271 (see FIG. 10). The refrigerant discharged in this way passes through the discharge pipe 1461 through the compressor discharge pipe 2281 and enters the condenser 143.

Although the first discharge valve 2271a is schematically shown in FIG. 10, the first discharge valve 2271a is installed directly above the discharge port 2271 and may operate on the same principle as a check valve that opens only above a preset pressure. have.

Referring to FIG. 10, the first discharge port 2231 is provided through the first bearing 2251, and the first discharge port 2251 is provided on the outer surface of the first bearing 2251 that does not contact the first cylinder 2211. A valve 2271a may be provided. The first discharge valve 2271a may be inserted into the groove of the first bearing in consideration of the effective area of the first discharge port and the thickness of the discharge port to open and close the first discharge port.

The first eccentric roller 2231 and the second eccentric roller 2232 may be provided so as to be eccentric around the drive shaft 214 in opposite directions. Since the first eccentric roller 2231 and the second eccentric roller 2232 can alternately compress and discharge the refrigerant with each other, the cycle of pressure change due to the discharge is reduced, thereby reducing vibration. In addition, since the degree of eccentricity around the axial direction of the drive shaft is the same, vibration and noise due to eccentricity can be reduced. In addition, it has the effect of reducing the load of celebration applied according to the change of the discharge pressure.

When the refrigerant is divided and compressed using two cylinders in this way, the ratio of the height-to-radius of the existing eccentric roller can be used less than one. Therefore, the size of the radius is smaller than the case of using only one eccentric roller with a height-to-radius ratio of less than 1, thus taking up less area, and the force applied to compress the same volume decreases with the moment of inertia due to the decreasing radius and height. The required torque is reduced.

In addition, there is an effect of reducing friction loss and leakage loss compared to conventional compressors having a height-to-radius of 1.2 to 1.6.

Considering that the stroke volume of the compressor must be 8cc/rev or more and 10cc/rev or less, the ratio of the height to radius of the eccentric rollers 2231 and 2232 may be 0.75 or more and 0.8 or less. Considering the range of the stroke volume described above in the compressor having two cylinders, the so-called twin compressor, the critical temperature of R-290, the specific volume, the leakage loss of the compressed refrigerant, the hydrodynamic losses such as friction in the pipeline inside the compressor, and This is the result of reflecting the valve opening and closing time of the discharge valve. For example, if the ratio of the height to the radius of the eccentric rollers 2231 and 2232 exceeds 0.8, the discharge valves 2271a and 2272a are opened for a long time to discharge more than the desired stroke volume, and if it is less than 0.75, the compressed refrigerant is As it is discharged, the pressure drop in the chambers 2291 and 2292 is rapid, so the desired stroke volume may not be discharged. In other words, the response speed of the discharge valve can also be a variable that influences this design. Considering these variables, the ratio of the height to the radius of the eccentric rollers 2231 and 2232 may be 0.75 or more and 0.8 or less.

With reference to FIG. 10, conditions necessary for optimal heat pump performance will be described. Fig. 10 is a cross-sectional view of section 8A in Fig. 8 by a dotted line. If the straight line passing through the center of the drive shaft 214 is L1 and the center of the first eccentric roller 2231 is L2, L2 is separated from L1 by a predetermined distance. The effective area (Q) of the first discharge port is, considering the critical pressure (4.25 MPa) and impingement temperature (97 ℃) of the flammable refrigerant R-290, the first discharge port (2271) and the second discharge port The effective area is preferably 25 mm2 or more and 26 mm2 or less, respectively. This is also the case with the second discharge port 2271.

In addition, it is preferable that the thickness of the first discharge port 2271 and the second discharge port is 1.5 mm or more and 2.5 mm or less, respectively. This is because if the thickness of the discharge port is too thick, friction loss occurs, and if it is too thin, it cannot withstand internal pressure.

In addition, considering the eccentric load and revolutions per minute generated by the first eccentric roller 2231 and the second eccentric roller 2232 on the drive shaft 214, in the case of cast iron, which is a material generally used for the drive shaft, the radius of the drive shaft ( rs) is preferably 5.5 mm to 7.5 mm.

If the eccentric roller is not a single member but is assembled by combining a cam and a roller, which is an eccentric part, it may be preferable that the cam and the roller have different heights so that the height of the cam is smaller than the height of the roller. This is to reduce unexpected friction with bearings or bulkheads due to tolerances during assembly. For example, if the height (hr) of the roller is 12 mm, the height of the cam can be set to 8.5 mm.

A brief description will be given of an oil passage part required for lubrication of a compressor using FIGS. 8 and 10. An oil passage part (not shown) including a first oil passage 261 penetrating in the axial direction of the drive shaft 214 is formed along the drive shaft 214, the first bearing 2251 and the second bearing 2252. I can.

The first oil passage 261 may be formed from one end to the other end of the drive shaft 214 to substantially penetrate the drive shaft 214 along the axial direction of the drive shaft. In addition, an oil and an oil pump (not shown) are provided at one end of the first oil passage 261 in the direction of the base unit 130. The oil pump (not shown) may be a kind of centrifugal pump.

The oil pump is immersed in oil, and accordingly, the oil can flow into the first flow path 261 through the oil pump. It is possible to flow into the first oil passage 261 through the oil pump 111. Thereafter, the oil may be pumped along the first oil passage 261 and scattered to be supplied from the end of the drive shaft 214 to each of the drive shafts 214, the first bearings 2251 and the second bearings 2252. .

In addition, the driving shaft around the first eccentric roller 2231 and the second eccentric roller 2232 so that oil can be supplied to the first oil passage 261 and the first eccentric roller 2231 and the second eccentric roller 2232 It may further include an oil hole (not shown) capable of communicating with the first oil passage 261 in the circumferential direction. In addition, it may include a second oil passage (not shown) that communicates with the oil hole to supply oil to the first bearing 2251 and the second bearing 2252. This may be formed as a groove formed in the inner circumferential surfaces of the first bearing 2251 and the second bearing 2252.

Oil (refrigerant oil) used in compressors is firstly used for lubricating action-lubrication of driving parts such as bearings and drive shafts, sliding parts of eccentric rollers and cylinders, and reduction of friction and wear. Second, it can also act as a sealing. Third, it can cool down, such as removing frictional heat. Fourth, it can have a rust prevention function to prevent oxidation of metal.

Since these oils are mixed with flammable refrigerants, they must have an appropriate solubility, and the better they have good viscosity and high flash point. The reason for having an adequate solubility is that the compressor oil volume is a factor that greatly affects the performance and reliability of the compressor and system. When the amount of oil is excessive due to a large amount of oil dissolved in the refrigerant, the reliability of the pump unit may deteriorate due to a decrease in efficiency due to an increase in temperature and abnormal high pressure due to a hydraulic shaft. In addition, this is because heat exchange is disturbed by the condenser, the function of the expansion valve is deteriorated, and heat exchange capacity decreases and pressure loss occurs due to the formation of an oil film in the evaporator pipe.

In particular, R-134a has polarity and is not well soluble in mineral oil, an existing oil. Therefore, a synthetic oil, polyester oil (hereinafter, POE oil) was used. Looking only at the aspect of lubrication, POE oil, which is a synthetic oil, may be good, but it has the following disadvantages. First, the moisture content is high when exposed to the atmosphere due to its good hygroscopicity, so it must be kept sealed. Therefore, when leakage occurs, it contains moisture, which may cause corrosion problems. Second, POE oil has a good cleaning effect, but it can cause failure by washing all kinds of lubricants, anti-rust coatings, and oxides generated during welding, emulsifying them and allowing them to flow along the refrigeration cycle.

Therefore, since the flammable refrigerant R290 has no polarity, it has an appropriate solubility (about 40% or more and 60% or less in the range of temperature and pressure during operation of the compressor), has excellent kinematic viscosity, and a mineral oil having a high flash point can be used. One such type of mineral oil is 5GSD. The kinematic viscosity is 95.11 ㎟/s based on 40 ℃, which is more than twice as high as the existing 4GSD and has a high flash point (194 ℃), so it can be used safely. In addition, the miscibility is good in the range of -50°C to 90°C, and the possibility of two-layer separation between oil and refrigerant is very low. The pour point is also low at about -25°C, making it suitable as an oil for a heat pump for the laundry treatment device. In the compressor 200, the 5GSD type oil filled amount may be preferably 220cc.

11 is related to the compressor motor 210. 11(a) and 11(c) show the stator 217 and the stator core of the conventional compressor motor.

8, a stator 217 of a compressor motor 210, a rotor 216 of a compressor motor, and a drive shaft 215 are included. The stator 217 of the compressor motor may include a lamination in which a ring-shaped electronic steel sheet (electric steel sheet or silicon steel sheet) is stacked and a coil 215 wound on the lamination. The rotor 216 of the compressor motor may also be provided by lamination in which electromagnetic steel sheets are stacked. The drive shaft 214 passes through the center of the rotor 216 of the compressor motor and is fixed to the rotor 216 of the compressor motor. When current is applied to the compressor 200, the rotor 216 of the compressor motor rotates due to mutual electromagnetic force between the stator 217 of the compressor motor 210 and the rotor 216 of the compressor motor, and the rotor 216 of the compressor motor rotates. The drive shaft 214 fixed to 216 is also a principle of rotating together.

Therefore, the rotational force of the compressor motor 210 may influence the performance of the compressor the most. In order to improve performance, the number of turns per unit area of the coil 215 may be increased, but there may be a limit in a narrow space. Accordingly, in the case of the compressor motor 210 according to an embodiment of the present invention as shown in FIG. 11(b), the stator may be provided with a two-stage core 2171 having a step as shown in FIG. 11(d). Through this, it is possible to increase the effective slot area, thereby improving loss due to copper loss and increasing magnetic flux flow. Accordingly, it is possible to improve the compressor efficiency and reduce the material cost compared to the conventional core without step difference.

Fig. 13 relates to a multi-stage compressor of refrigerant in multiple stages unlike a twin compressor. Since the case of compressing the refrigerant in multiple stages requires much less work than the case of compressing the refrigerant to a desired pressure at once, the performance of the heat pump can be improved accordingly. To this end, the second cylinder 2212 compresses the refrigerant at low pressure, and the first cylinder 2211 compresses the refrigerant at high pressure. In this embodiment, the functions of the first cylinder 2211 and the second cylinder 2212 may be changed. In FIG. 13, refrigerant flows into the second cylinder 2212 through the second inlet 2811, and the refrigerant compressed in the second cylinder 2212 is discharged through the third inlet 2810, and then the intermediate connection ( 2813) and the first inlet 2811 may be introduced into the first cylinder 2211. The first cylinder may compress the refrigerant again at a higher pressure than the second cylinder to reach a desired condensing pressure, and then discharge the refrigerant to the condenser through the compressor discharge pipe 2281.

14 is a condenser 143 of a heat pump 140 provided in a clothes treatment apparatus using a flammable refrigerant according to an embodiment of the present invention.

The condenser 143 located inside the duct 120 may heat air by transferring heat generated by condensing the refrigerant compressed by the compressor 200 to the air passing through the condenser 143. The condenser 143 may include a first condensed substrate 1431 and a second condensed substrate 1432 positioned on both sides of the duct 120. The condenser pipe 1433 through which the refrigerant flows is supported through the first condensed substrate 1431 and the second condensed substrate 1432. The condenser pipe is repeatedly reciprocated a plurality of times while maintaining a predetermined distance between the first condensed substrate 1431 and the second condensed substrate 1432 to form a single connected pipe. ) Can be connected. In addition, a plurality of condenser radiating fins 1434 may be included between the first condensed substrate 1431 and the second condensed substrate 1432 in the same direction as the first condensed substrate and the second condensed substrate.

Therefore, when the condenser pipe 1433 reciprocates between the first condensed substrate 1431 and the second condensed substrate 1432, it passes through the plurality of condenser radiating fins 1434, and the plurality of condenser radiating fins 1434 is a condenser. The portion through which the pipe 1433 passes and the condenser pipe 1433 may be coupled to allow heat exchange. Therefore, as the high-temperature refrigerant passes through the condenser pipe 1433, heat is transferred to the plurality of condenser radiating fins 1434, and the heat is transferred to the air passing between the plurality of radiating fins.

In other words, when air flows in the direction of the arrow (the direction of the first flow path to the third flow path, the direction from the front to the rear of the duct, or the length direction of the duct), a condenser pipe installed in a direction crossing both sides of the duct The high-temperature refrigerant passing through (1433) can transfer heat to the relatively low-temperature air.

Compared to R-134a, R-290 has a larger specific volume, but the amount of charging used is small, so the overall volume is smaller. Therefore, if the condenser pipe 1433 having the same diameter and length as the condenser used in the existing R-134a is used, the condenser pipe is in a subcooled state at the outlet 1433b. In order to prevent this, the diameter of the condenser pipe 1433 may be designed to be small. Preferably, the diameter of the condenser pipe 1433 may be 5 mm.

As the diameter of the condenser pipe 1433 decreases, the refrigerant flowing through the inside passes at a higher speed, so that the amount of heat transfer per hour increases. In addition, when the diameter of the condenser pipe 1433 is decreased, the flow cross-sectional area through which air actually passes in the condenser 143 increases, so that more air can pass through the condenser 143. Therefore, it may be desirable to increase the FPI (Fin per inch) representing the number of fins per inch of the condenser radiating fins 1434 than the FPI in the existing R-134a. For example, 16 FPI is available on the conventional R-134a, while 18 FPI is available on the condenser used on the R-290.

In addition, since the amount of heat transfer increases, the length L of the condenser may be shorter than that of the condenser used in R-134a. This means that the condenser 142 is miniaturized. That is, the internal volume of the condenser 142 is reduced by about 50% compared to the internal volume of the condenser in R134-a.

In addition, the number of condenser pipes passing through the first condensed substrate 1421 and the second condensed substrate 1422 from the side of the duct 120 may be arranged more by reducing the diameter of the condenser pipe. For example, if the arrangement of the condenser pipes in the existing R-134a is 8 and 5 (8R × 5C) in the longitudinal direction and the height direction of the first condensing board, the arrangement of the condenser pipes in R-290 is the first. It can be arranged in eight and six (8R × 6C) based on the length direction (L) and height direction (T) of the condensing substrate. In addition, dL and dT indicating the distance between adjacent condenser pipes 1431 may be set equally.

When the amount of heat transfer equivalent increases, the pressure difference (ΔP) of air passing through the condenser also increases, and the flow rate of air may increase. Preferably, the flow rate of air may have 2 to 3 m/s.

15 relates to an evaporator 142 of a heat pump 140 provided in a clothes treatment apparatus using a flammable refrigerant according to an embodiment of the present invention.

The evaporator 142 located inside the duct 120 is a device that transfers heat to the refrigerant through heat exchange with the hot and humid air introduced from the drum 110 and evaporates the refrigerant again. At this time, the high-temperature and high-humidity air becomes relatively low-temperature dehumidified air while passing through the evaporator 142.

The evaporator 142 may include a first evaporator plate 1421 and a second evaporator plate 1422 positioned on both sides of the duct 120. The evaporator pipe 1423 through which the refrigerant flows is supported through the first evaporation substrate 1421 and the second evaporation substrate 1422. The evaporator pipe 1423 repeats a plurality of times while maintaining a certain distance between the first evaporation substrate 1421 and the second evaporation substrate 1422, and the first evaporation substrate 1421 and the second evaporation through a single connected pipe. It is possible to connect between the substrates 1422. In addition, a plurality of evaporator heat dissipation fins 1424 may be included in the same direction as the first evaporation substrate 1421 and the second evaporation substrate 1422 between the first evaporation substrate 1421 and the second evaporation substrate 1422.

Therefore, when the evaporator pipe 1423 reciprocates between the first evaporator plate 1421 and the second evaporator plate 1422, it passes through the plurality of evaporator radiating fins 1424, and the plurality of evaporator radiating fins 1424 is an evaporator. The portion through which the pipe 1423 passes and the evaporator pipe 1423 may be coupled to each other such that heat transfer is possible. Therefore, when relatively high temperature air passes through the evaporator 142, heat is transferred by the plurality of evaporator heat dissipation fins 1424, and this heat is transferred to the evaporator pipe 1423 through which the relatively low temperature refrigerant passes. It is a principle.

In other words, when air flows in the direction of the arrow (the direction of the first flow path to the third flow path, the direction from the front to the rear of the duct, or the length direction of the duct), an evaporator pipe installed in a direction crossing both sides of the duct The low temperature refrigerant passing through 1423 may receive heat from the relatively high temperature air.

Compared to R-134a, R-290 has a larger specific volume, but the amount of charging used is small, so the overall volume is smaller. Therefore, if the evaporator pipe 1423 having the same diameter and length as the evaporator 142 used in the existing R-134a is used, the evaporator pipe becomes a supersaturated vapor state at the outlet 1422b of the evaporator pipe. This soon increases the energy consumption of the compressor or damages the compressor. In order to prevent this, the diameter of the evaporator pipe 1423 may be designed to be small. However, it may be designed to be larger than the diameter of the condenser pipe 1433. This is because the temperature difference between the refrigerant heat exchanged in the condenser and air is greater than the temperature difference between the refrigerant heat exchanged in the evaporator. Therefore, the diameter of the evaporator pipe 1423 may be designed to be larger than the diameter of the condenser pipe 1433 in order to achieve sufficient heat transfer by slowing the flow rate of the refrigerant inside the evaporator. Preferably, the diameter of the evaporator pipe 1423 may be 7.94mm.

The low-temperature refrigerant passes through the inside of the evaporator pipe 1423 having a smaller diameter at a higher speed, so that the amount of heat transfer per hour increases. In addition, when the diameter of the evaporator pipe 1423 is decreased, the flow cross-sectional area through which air actually passes in the evaporator 142 increases, so that more air can pass through the evaporator 142, so that heat transfer can be improved.

When the amount of heat transfer equivalent increases, the pressure difference (ΔP) of air passing through the condenser also increases, and the flow rate of air may increase. Preferably, the flow rate of air may have 2 to 3 m/s.

To this end, the thickness of the evaporator heat sink 1424 may be thinner than that of the evaporator heat sink when R-134a is used. For example, if the thickness of the existing evaporator radiating fins 1424 was 0.14 mm, the thickness of the evaporator radiating fins 1424 in R290 may be 0.13 mm or less, preferably 0.1 mm. In addition, the dehumidified moisture may be attached to the evaporator heat dissipation fin 1423. This soon deteriorates the heat exchange performance of the evaporator heat sink 1424. Therefore, in order to prevent this, the evaporator heat dissipation fin 1424 may be coated with a hydrophilic property.

In addition, since the amount of heat transfer increases, the length L of the duct may be shorter than that of the evaporator used in R-134a. This means that the evaporator 142 is miniaturized. That is, the internal volume of the evaporator 142 is reduced by about 30% compared to the internal volume of the evaporator in R134-a.

In addition, the number of arrangements of the evaporator pipes 1423 passing through the first evaporation substrate 1421 and the second evaporation substrate 1422 from the side of the duct 120 may be more arranged by reducing the diameter of the condenser pipe. In the R-290, the evaporator pipes 1423 may be arranged in 5 and 4 (5R×4C) length directions (L) and height directions (T) of the first evaporator plate 1421. In addition, dL and dT indicating the distance between the adjacent evaporator pipes 1423 may be constant.

The condenser pipe inlet (1431a) and the condenser pipe outlet (1431b), and the evaporator pipe inlet (1421a) and the evaporator pipe outlet (1421b) pass through the side of the duct 120 and the expansion part 145 outside the duct 120 And the compressor 200 and the refrigerant pipe 146 may be connected.

16 is a refrigerant pipe 146 for circulating a flammable refrigerant in a heat pump 140 provided in a clothes treatment apparatus using a flammable refrigerant according to an embodiment of the present invention.

Figure 16 (a) is a diagram showing the connection of the refrigerant pipe and the expansion unit, (b) is an expansion unit (c) is a discharge pipe (d) is an embodiment of a suction pipe.

Referring to Figure 16(a), the refrigerant pipe for circulating the refrigerant includes a discharge pipe 1461 connecting the compressor 200 and the condenser 142, and an expansion unit 145 connecting the condenser 142 and the evaporator 143. ), a suction pipe 1462 connecting the evaporator 142 to the accumulator 280 of the compressor 200.

Fig. 16(b) shows an expansion part 145 used in a laundry treatment apparatus according to an embodiment of the present invention. This is only an embodiment, and the shape and length of the pipe can be modified and used unless otherwise specified. The expansion unit 145 may include an expansion valve or a capillary tube 1464 for expanding the condensed refrigerant. In addition, in order to remove foreign substances that may be included in the condensed refrigerant, it may pass through the filter dryer 1465 before the capillary tube 1464. The evaporator connection part 1451a of the expansion part connected to the inlet 1421a of the evaporator pipe is combined by expanding the diameter of the expansion part in consideration of the diameter of the evaporator pipe 1423. The diameter of the expansion portion is not tapered continuous expansion, but has a shape expanded in stages while having at least one step difference. This is to prevent the refrigerant from leaking by combining the inlet 1421a of the evaporator pipe and the evaporator connector 1451a of the expansion unit through a wide surface contact. Preferably, the inlet 1421a of the evaporator pipe and the evaporator connection part 1451a of the expansion part may be connected by welding.

In addition, the length of the capillary tube 1464 is shorter than the length of the capillary tube 1464 used in the pressure drop R-134a because the ratio of the pressure drop per capillary length of R-290 is faster than R-134a and is similar to that of Freon gas. I can lose. Therefore, it may be preferably 1300 mm. However, since there may be an error in the amount of filling R-290 is charged to the compressor, the length of the capillary tube 1464 may be 1250 mm or more and 1350 mm or less.

Fig. 16(c) shows a discharge pipe 1461 used in a laundry treatment apparatus according to an embodiment of the present invention. The condenser connection part 1461a of the discharge pipe connected to the inlet 1431a of the condenser pipe is gradually reduced in diameter by at least one or more steps to match the diameter of the condenser pipe. This is to prevent the refrigerant from leaking out by combining the inlet (1431a) of the condenser pipe and the condenser connector (1461a) of the discharge pipe through wide surface contact. Preferably, the inlet (1431a) of the condenser pipe and the condenser connection portion (1461a) of the discharge pipe may be connected by welding.

Fig. 16(d) shows a suction pipe 1462 used in a laundry treatment apparatus according to an embodiment of the present invention. The evaporator connection 1462a of the suction pipe connected to the outlet 1421b of the evaporator pipe is gradually reduced in diameter by at least one step or more in order to match the diameter of the evaporator pipe 1423. This is to prevent the refrigerant from leaking by combining the outlet 1421b of the evaporator pipe and the evaporator connection 1462a of the suction pipe through a wide surface contact. Preferably, the outlet 1421b of the evaporator pipe and the evaporator connection 1462a of the suction pipe may be connected by welding.

In the present specification, a specific embodiment has been illustrated, and it is understood that the shown specific embodiment can be replaced with any reconstruction calculated to achieve the same purpose, and the disclosed invention can be applied differently in other environments. It will be self-explanatory to the technician. That is, this application should be understood to cover any application or change to the disclosure of the present invention. The claims that follow are not intended to be limited to the scope of the disclosure relating to specific embodiments of the present specification. Therefore, if the modified embodiment includes the elements of the claims of the present invention, it should be viewed as belonging to the scope of the present invention.

100 clothes handling equipment
101 cabinet 104 control panel 106 slot
108 Door 1081 Door hinge 1082 Magnetic part
1083 Sensing unit 109 Display unit
104 Front supporter 1041 Outlet 1042 Opening
105 Rear porter 1051 Inlet 1052 Rear protrusion
110 drum 120 duct
1210 Front Duct 1211 Filter Guide
230 rear duct 1231 rear duct connector
124 Filter 1242 Filter installation part
127 Ventilation fan installation part 128 Cover plate
130 base
140 Heat pump 200 Compressor 2001 Box fan
142 evaporator 1423 evaporator pipe
143 Condenser 1433 Condenser pipe
145 Expansion part 146 Refrigerant tube 1464 Capillary tube
200 Compressor 203 Compressor case 214 Crank shaft 2141 Eccentric part 220 Compression part 221 Cylinder
2223 bulkhead 2231 1st eccentric roller 2232 2nd eccentric roller
2241 First vane 2242 Second vane
2251 First bearing 2252 Second bearing
226 Noise reduction part 227 Compressor discharge part
2271 1st discharge port 2271a 1st discharge valve
2272 2nd discharge port 2272a 2nd discharge valve 2273 Discharge connection 228 Compressor inlet
2281 1st inlet port 2282 2nd inlet port
2291 Chamber 1 2292 Chamber 2

Claims (27)

Compressor case;
A circular first cylinder positioned inside the compressor case to provide a first chamber;
A circular second cylinder positioned inside the compressor case to provide a second chamber;
A diaphragm disposed between the first and second cylinders and separating the first and second chambers;
A first eccentric roller located in the first chamber and rotatable in contact with the inner circumferential surface of the first cylinder, and a second eccentric roller located in the second chamber and rotatable in contact with the inner circumferential surface of the second cylinder, and the first A cylinder, a drive shaft passing through the second cylinder and the diaphragm;
A first vane having one end fixed to the first cylinder, the other end contacting the first eccentric roller, and installed to enable a reciprocating motion when the first eccentric roller rotates;
A second vane having one end fixed to the second cylinder, the other end contacting the second eccentric roller, and installed to enable a reciprocating motion when the second eccentric roller rotates;
A first inlet port through which the refrigerant flows into the first chamber through the first cylinder;
A second inlet port through which the refrigerant flows into the second chamber through the second cylinder;
A compressor discharge unit including a first discharge port for discharging the refrigerant in the first chamber and a second discharge port for discharging the refrigerant in the second chamber; and
The first eccentric roller and the second eccentric roller
Compressor, characterized in that the height-to-radius ratio (Height-to-radius ratio) is 0.75 or more and 0.8 or less, respectively.
The method of claim 1,
Compressor, characterized in that the stroke volume of the compressor is 8 cc/revolution or more and 10 cc/revolution or less.
The method of claim 1,
The eccentricity of the first eccentric roller and the second eccentric roller are located in opposite directions with respect to the drive shaft,
The compressor, characterized in that the first discharge port and the second discharge port alternately discharge the compressed refrigerant during one rotation of the drive shaft.
The method of claim 1,
Further comprising a power generating unit for rotating the drive shaft,
The power generating unit includes a compressor motor that generates rotational force by electromagnetic force,
The compressor motor includes a rotor coupled to the drive shaft and a stator wound with a coil.
The method according to any one of claims 1 to 4,
A first bearing coupled to one surface of the first cylinder located in a direction away from the diaphragm to rotatably support the drive shaft;
A second bearing coupled to one surface of the second cylinder positioned in a direction away from the diaphragm to rotatably support the drive shaft; further comprising,
The first discharge port is
Discharge the refrigerant in the first chamber through the first bearing,
The second discharge port is
Discharge the refrigerant in the second chamber through the second bearing,
The compressor discharge unit
A first discharge valve positioned on the first bearing to discharge only when a pressure of the refrigerant discharged through the first discharge port is equal to or higher than a preset pressure;
A second discharge valve positioned on the second bearing and configured to discharge only when the pressure of the refrigerant discharged through the second discharge port is equal to or higher than a preset pressure; Compressor characterized in that it further comprises.
The method of claim 5,
The compressor, characterized in that the effective areas of the first discharge port and the second discharge port are 25 mm2 or more and 26 mm2 or less, respectively.
The method of claim 6,
The compressor, wherein the first discharge port and the second discharge port have a thickness of 1.5 mm or more and 2.5 mm or less, respectively.
The method of claim 1,
Compressor, characterized in that the radius of the drive shaft is 5.5 mm to 7.5 mm.
The method of claim 4,
An oil passage part supplying oil to lubricate the drive shaft, the power generating part, the first vane, the second vane, the first eccentric roller, the second eccentric roller, the first bearing, and the second bearing; Compressor characterized in that it further comprises.
The method of claim 1,
The compressor, characterized in that the refrigerant is a flammable refrigerant.
Ducts for inflow and outflow of air;
An evaporator located inside the duct and cooling the air introduced into the duct;
A condenser located inside the duct and heating air that has passed through the evaporator;
A compressor located outside the duct, compressing the refrigerant passing through the evaporator and supplying it to the condenser;
A refrigerant pipe in communication with the evaporator, the condenser and the compressor through which the refrigerant flows; and
The compressor
Compressor case;
A circular first cylinder positioned inside the compressor case to provide a first chamber;
A circular second cylinder positioned inside the compressor case to provide a second chamber;
A diaphragm disposed between the first and second cylinders and separating the first and second chambers;
A first eccentric roller located in the first chamber and rotatable in contact with the inner circumferential surface of the first cylinder, and a second eccentric roller located in the second chamber and rotatable in contact with the inner circumferential surface of the second cylinder, and the first A cylinder, a drive shaft passing through the second cylinder and the diaphragm;
A first vane having one end fixed to the first cylinder, the other end contacting the first eccentric roller, and installed to enable a reciprocating motion when the first eccentric roller rotates;
A second vane having one end fixed to the second cylinder, the other end contacting the second eccentric roller, and installed to enable a reciprocating motion when the second eccentric roller rotates;
A first inlet port through which the refrigerant flows into the first chamber through the first cylinder;
A second inlet port through which the refrigerant flows into the second chamber through the second cylinder;
A compressor discharge unit including a first discharge port for discharging the refrigerant in the first chamber and a second discharge port for discharging the refrigerant in the second chamber; and
The first eccentric roller and the second eccentric roller
Each of the heat pump, characterized in that the height-to-radius ratio (Height-to-radius ratio) is 0.75 or more and 0.8 or less.
The method of claim 11,
A heat pump, characterized in that the stroke volume of the compressor is 8 cc/revolution or more and 10 cc/revolution or less.
The method of claim 11,
The eccentricity of the first eccentric roller and the second eccentric roller are located in opposite directions with respect to the drive shaft,
The heat pump, characterized in that the first discharge port and the second discharge port alternately discharge the compressed refrigerant upon one rotation of the drive shaft.
The method according to any one of claims 11 to 13,
A first bearing coupled to one surface of the first cylinder located in a direction away from the diaphragm to rotatably support the drive shaft;
A second bearing coupled to one surface of the second cylinder positioned in a direction away from the diaphragm to rotatably support the drive shaft; further comprising,
The first discharge port is
Discharge the refrigerant in the first chamber through the first bearing,
The second discharge port is
Discharge the refrigerant in the second chamber through the second bearing,
The compressor discharge unit
A first discharge valve positioned on the first bearing to discharge only when a pressure of the refrigerant discharged through the first discharge port is equal to or higher than a preset pressure;
A second discharge valve positioned on the second bearing and configured to discharge only when the pressure of the refrigerant discharged through the second discharge port is equal to or higher than a preset pressure; Heat pump, characterized in that it further comprises.
The method of claim 14,
The heat pump, wherein the effective areas of the first discharge port and the second discharge port are 25 mm2 or more and 26 mm2 or less, respectively.
The method of claim 15,
The heat pump, characterized in that the thickness of the first discharge port and the second discharge port is 1.5 mm or more and 2.5 mm or less, respectively.
The method of claim 11,
Heat pump, characterized in that the radius of the drive shaft is 5.5 mm to 7.5 mm.
The method of claim 11,
The refrigerant is a heat pump, characterized in that the flammable refrigerant.
The method of claim 18,
Heat pump, characterized in that the flammable refrigerant is R-290.
The method of claim 11,
The compressor
Further comprising a; power generating unit for rotating the drive shaft,
An oil passage part supplying oil to lubricate the drive shaft, the power generating part, the first vane, the second vane, the first eccentric roller, the second eccentric roller, the first bearing, and the second bearing; Heat pump, characterized in that it further comprises.
The method of claim 20,
The oil is a heat pump, characterized in that the 5GSD type.
The method of claim 11,
The evaporator is
A plurality of evaporator radiating fins for heat exchange with a plate shape
It includes an evaporator pipe passing through the plurality of evaporator radiating fins and reciprocating a plurality of times,
The refrigerant is discharged to the compressor after the refrigerant flowing through the condenser flows into and exchanges heat with air,
The evaporator heat sink is a heat pump, characterized in that the hydrophilic coating to prevent the moisture condensed in the air from adhering to the evaporator heat sink.
The method of claim 23,
The condenser is
Plate shape, multiple condenser radiating fins for heat exchange
It includes a condenser pipe passing through the plurality of condenser radiating fins and reciprocating a plurality of times,
The refrigerant is discharged to the evaporator after the refrigerant passing through the compressor flows in and heat exchange with air,
Heat pump, characterized in that the diameter of the condenser pipe is smaller than the diameter of the evaporator pipe.
The method of claim 11,
The refrigerant pipe is
A suction pipe connecting the evaporator and the compressor;
A discharge pipe connecting the compressor and the condenser;
Including; an expansion unit connecting between the evaporator and the compressor,
The expansion unit includes a capillary tube for lowering the pressure of the refrigerant,
Heat pump, characterized in that the length of the capillary tube is 1250mm or more and 1350mm or less.
Cabinets forming the exterior;
A cylindrical drum located inside the cabinet;
A duct for circulating air in the drum;
An evaporator located inside the duct and cooling the air introduced into the duct;
A condenser located inside the duct and heating air that has passed through the evaporator;
A compressor located outside the duct, compressing the refrigerant passing through the evaporator and supplying it to the condenser;
A refrigerant pipe in communication with the evaporator, the condenser and the compressor through which the refrigerant flows; and
The compressor
Compressor case;
A circular first cylinder positioned inside the compressor case to provide a first chamber;
A circular second cylinder positioned inside the compressor case to provide a second chamber;
A diaphragm disposed between the first and second cylinders and separating the first and second chambers;
A first eccentric roller located in the first chamber and rotatable in contact with the inner circumferential surface of the first cylinder, and a second eccentric roller located in the second chamber and rotatable in contact with the inner circumferential surface of the second cylinder, and the first A cylinder, a drive shaft passing through the second cylinder and the diaphragm;
A first vane having one end fixed to the first cylinder, the other end contacting the first eccentric roller, and installed to enable a reciprocating motion when the first eccentric roller rotates;
A second vane having one end fixed to the second cylinder, the other end in contact with the second eccentric roller, and installed to enable a reciprocating motion when the second eccentric roller rotates;
A first inlet port through which the refrigerant flows into the first chamber through the first cylinder;
A second inlet port through which the refrigerant flows into the second chamber through the second cylinder;
A compressor discharge unit including a first discharge port for discharging the refrigerant in the first chamber and a second discharge port for discharging the refrigerant in the second chamber; and
The first eccentric roller and the second eccentric roller
Clothing treatment apparatus, characterized in that the height-to-radius ratio (Height-to-radius ratio) is 0.75 to 0.8, respectively.
The method of claim 25.
Clothing treatment apparatus, characterized in that the refrigerant is R-290.
The method of claim 26,
A first bearing coupled to one surface of the first cylinder located in a direction away from the diaphragm to rotatably support the drive shaft;
A second bearing coupled to one surface of the second cylinder positioned in a direction away from the diaphragm to rotatably support the drive shaft; further comprising,
The first discharge port is
Discharge the refrigerant in the first chamber through the first bearing,
The second discharge port is
Discharge the refrigerant in the second chamber through the second bearing,
The compressor discharge unit
A first discharge valve positioned on the first bearing to discharge only when a pressure of the refrigerant discharged through the first discharge port is equal to or higher than a preset pressure;
A second discharge valve positioned on the second bearing and configured to discharge only when the pressure of the refrigerant discharged through the second discharge port is equal to or higher than a preset pressure; Clothing treatment apparatus further comprising a.

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