Patent Description:
A compressor, which is one of the elements constituting a refrigeration cycle device, is a device for converting a low-temperature low-pressure refrigerant gas to a high-temperature high-pressure gas by using power of a rotation shaft received from an electric motor. In a structure where a driving unit and a compression unit are sealed in a casing, the compressor may be instantaneously stopped due to various causes such as external electric shocks, excessive refrigerant intake flow rates, abnormal behaviors of a valve, pressure pulsations in a cycle, etc..

In this case where the compressor operation is stopped, there may be a difference in pressure between an internal space of the compressor with relatively high pressure and a compression chamber with relatively low pressure because a discharge flow path to discharge the refrigerant gas of the compression chamber to the internal space of the compressor is blocked by a discharge valve.

When the pressure difference is not resolved, refrigerant backflow, oil leakage, and the like may occur. Furthermore, when re-operation of the compressor is attempted while the pressure in the internal space and the pressure in the compression chamber do not reach a pressure equilibrium (balanced pressure) after the compressor is stopped, the difference between the pressure in the internal space and the pressure in the compression chamber is greater than a pressure difference at which the compressor can be operated, and thus the re-operation of the compressor might fail. Besides, when the compressor is re-operated, a lot of time and energy may be consumed in order for the refrigeration cycle to return to a stable state. Hence, there may be a need for a device enabling evaporation pressure and condensing pressure to quickly reach a balanced pressure when the compressor is stopped.

In other words, a device for the compressor and refrigeration cycle device having the compressor in which a pressure balance in the compressor may be obtained quickly to prevent refrigerant backflow and oil leaks and so that the compressor can be re-operated or restarted quickly.

Additional aspects will be set forth in part in the description which follows and, in part, will be apparent from the description, or may be learned by practice of the example embodiments.

Aspects of the disclosure may be directed to a device for the compressor and for a refrigeration cycle device having the compressor, in which a pressure balance in the compressor may be obtained quickly to prevent refrigerant backflow and oil leaks and so that the compressor can be re-operated or restarted quickly.

According to aspects of the invention, there is provided a compressor as set out in claim <NUM> and a refrigeration cycle device as set out in claim <NUM>. In accordance with an aspect of the disclosure, a compressor may include a casing, a driving unit disposed in the casing, a compression unit coupled to the driving unit and configured to compress a refrigerant, and a valve configured to control a flow of the refrigerant in the casing. The valve may include a valve chamber including a main flow path, in which the refrigerant is to flow, the main flow path including a refrigerant inlet and a refrigerant outlet, a floating body disposed in the valve chamber to open or close the main flow path, and a bypass flow path formed in the valve chamber and to be opened or closed by the floating body. When the driving unit is stopped and the bypass flow path is opened by the floating body, the bypass flow path is to allow the refrigerant to be detoured to the bypass flow path.

When the driving unit is operated during operation of the compressor, the floating body may be configured to open the main flow path. When the driving unit (or compressor) is stopped, the floating body may be configured to close the main flow path and open the bypass flow path.

The bypass flow path may include a bypass inlet and a bypass outlet. When the driving unit is operated during operation of the compressor, the floating body may be configured to close at least one of the bypass inlet and the bypass outlet. When the driving unit (or compressor) is stopped, the floating body may be configured to close at least one of the refrigerant inlet and the refrigerant outlet.

The valve may further include an elastic member configured to elastically pressurize the floating body such that the floating body closes the refrigerant inlet when the driving unit (or compressor) is stopped.

The compressor may further include a sealing member disposed between the valve chamber and the floating body to prevent the refrigerant from leaking into the bypass flow path during operation of the compressor (or driving unit).

The refrigerant inlet may be formed at a lower (bottom) portion of the valve chamber, and the refrigerant outlet may be formed at an upper (top) portion of the valve chamber. The elastic member may be disposed between the upper portion of the valve chamber and the floating body, and the bypass flow path may be disposed along a circumferential surface of the floating body.

The floating body may include a plurality of floating bodies, and the plurality of floating bodies may include a first floating body disposed in an upper portion of the valve chamber and a second floating body disposed below the first floating body.

The valve may further include a fixed body disposed in the valve chamber to allow the refrigerant to flow along the main flow path or the bypass flow path. The first floating body may be disposed above (on top of) the fixed body to open or close the main flow path, and the second floating body may be disposed in an internal space of the fixed body to open or close the bypass flow path.

The plurality of floating bodies may each include a hollow portion. The first floating body may include a first floating body hollow portion formed to be smaller than the refrigerant outlet of the valve chamber, and the second floating body may include a second floating body hollow portion formed to be smaller than an inlet of the fixed body.

The floating body may include a first floating body disposed on a first side of the valve chamber and a second floating body disposed on a second side of the valve chamber. The bypass flow path may be formed between the valve chamber and at least one of the first floating body and the second floating body, and the compressor may further include a sealing member disposed in an area where the bypass flow path is formed to prevent the refrigerant from leaking from the bypass flow path when the driving unit (or compressor) is stopped.

The compressor may include a compression chamber configured to compress the refrigerant, and a refrigerant suction tube configured to suck the refrigerant into the compression chamber. The valve may be disposed between an internal space of the casing and the refrigerant suction tube so that the bypass flow path discharges (or releases) the refrigerant from the internal space of the casing into the refrigerant suction tube.

In accordance with an aspect of the disclosure, a refrigeration cycle device may include a condenser, an expander connected to the condenser, an evaporator connected to the expander, a compressor connected to the evaporator and configured to compress a refrigerant, and a valve disposed on at least one of an outside or an inside of the compressor and configured to control a flow of the refrigerant in the compressor. The valve may include a valve chamber including a refrigerant inlet and a refrigerant outlet, a floating body, disposed in the valve chamber, configured to control a flow of the refrigerant into the valve chamber and a flow of the refrigerant out of the valve chamber, and a bypass flow path formed in the valve chamber to be opened or closed based on a movement of the floating body. When the compressor is stopped and the bypass flow path is opened based on the movement of the floating body, the bypass flow path may allow the refrigerant to be detoured to the bypass flow path which includes a bypass inlet and a bypass outlet.

The floating body may be configured to close the bypass flow path when the compressor (or driving unit) is operated (during an operation of the compressor or driving unit), and may be configured to open the bypass flow path when the compressor (or driving unit) is stopped.

The valve may further include a main flow path formed in the valve chamber to allow the refrigerant to flow from the refrigerant inlet to the refrigerant outlet. The valve may further include an elastic member configured to elastically pressurize a main flow path formed in the valve chamber and the floating body, and the elastic member may be disposed between the valve chamber and the floating body so that the floating body closes the main flow path when the compressor (or driving unit) is stopped.

In accordance with an aspect of the disclosure, a refrigeration cycle device may include a condenser, an expander connected to the condenser, an evaporator connected to the expander, a compressor connected to the evaporator, and a valve arranged or disposed on at least one of an outside and an inside of the compressor. The valve may include a valve case, a floating body disposed in the valve case, a main flow path formed in the valve case and including a refrigerant inlet and a refrigerant outlet to allow a refrigerant to flow, and a bypass flow path including a bypass inlet and a bypass outlet for the refrigerant to be detoured to the bypass flow path when the main flow path is blocked or closed. The floating body may open the main flow path and block or close the bypass flow path during an operation of the compressor, and block or close the main flow path and open the bypass flow path when the compressor is stopped.

The bypass flow path may be formed between the valve case and the floating body.

The floating body may close or block at least one of the bypass inlet and the bypass outlet during an operation of the compressor or driving unit, and the floating body may close or block at least one of the refrigerant inlet or the refrigerant outlet when the compressor (or driving unit) is stopped.

An elastic member may be arranged or disposed between the valve case and the floating body and configured to elastically pressurize the floating body such that the floating body blocks or closes the refrigerant inlet when the compressor or driving unit is stopped.

The valve may further include a sealing member arranged or disposed between the valve case and the floating body to prevent the refrigerant from leaking into the bypass flow path during an operation of the compressor.

An aspect of the disclosure provides a compressor and refrigeration cycle device having the same, capable of efficiently removing a compression load in a compressor casing.

Another aspect of the disclosure provides a compressor and refrigeration cycle device having the same, capable of quickly reaching a pressure equilibrium in a compressor casing for re-operation from a stopped state.

Another aspect of the disclosure provides a compressor and refrigeration cycle device with reduced material costs and manufacturing costs.

Embodiments and features as described and illustrated in the disclosure are merely examples, and there may be various modifications to replace the embodiments and drawings of the disclosure.

The terminology used herein is for the purpose of describing example embodiments and is not intended to limit the disclosure.

The terms including ordinal numbers like "first" and "second" may be used to explain various components, but the components are not limited by the terms. The terms are only for the purpose of distinguishing a component from another. Thus, a first element, component, region, layer or room discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the disclosure. Descriptions shall be understood as to include any and all combinations of one or more of the associated listed items when the items are described by using the conjunctive term "and/or," or the like. That is, the term "and/or" includes a plurality of combinations of relevant items or any one item among a plurality of relevant items. For example, the scope of the expression or phrase "A and/or B" includes all of the following: (<NUM>) the item "A", (<NUM>) the item "B", and (<NUM>) the combination of items "A and B".

In addition, the scope of the expression or phrase "at least one of A and B" is intended to include all of the following: (<NUM>) at least one of A, (<NUM>) at least one of B, and (<NUM>) at least one A and at least one of B. Likewise, the scope of the expression or phrase "at least one of A, B, and C" is intended to include all of the following: (<NUM>) at least one of A, (<NUM>) at least one of B, (<NUM>) at least one of C, (<NUM>) at least one of A and at least one of B, (<NUM>) at least one of A and at least one of C, (<NUM>) at least one of B and at least one of C, and (<NUM>) at least one of A, at least one of B, and at least one of C.

When it is stated in the disclosure that one element is "connected to" or "coupled to" another element, the expression encompasses an example of a direct connection or direct coupling, as well as a connection or coupling with another element interposed therebetween.

The terms "forward (or front)", "rearward (or rear)", "left", and "right" as herein used are defined with respect to the drawings, but the terms may not restrict the shape and position of the respective components.

Reference will now be made in detail to embodiments of the disclosure, which are illustrated in the accompanying drawings, wherein like reference numerals refer to the like elements throughout.

According to the disclosure, a compressor and refrigeration cycle device including the same may be provided, which uses a simple structure to maintain a balanced pressure as soon as possible in a stopped state by removing a compression load in the compressor.

According to the disclosure, a compressor and refrigeration cycle device with reduced material cost and manufacturing cost may be provided.

<FIG> shows a refrigeration cycle device, according to an embodiment of the disclosure.

Referring to <FIG>, a refrigeration cycle device <NUM> includes a compressor <NUM>, a condenser <NUM>, an expander <NUM>, and an evaporator <NUM>. The refrigeration cycle device <NUM> may allow a refrigerant to circulate a series of processes of compression, condensing, expansion, and evaporation, and make the refrigerant and an object to be cooled exchange heat with each other to cool the object.

The compressor <NUM> compresses a refrigerant gas into a high-temperature and high-pressure state and discharges the refrigerant gas, and the discharged refrigerant gas flows into the condenser <NUM>. The condenser <NUM> condenses the compressed refrigerant into a liquid state, and radiates heat to the surroundings through the condensing process.

The expander <NUM> expands the high-temperature and high-pressure liquid refrigerant condensed by the condenser <NUM> to low-pressure liquid refrigerant. The evaporator <NUM> evaporates the refrigerant expanded by the expander <NUM>. The evaporator <NUM> achieves a cooling effect by using latent heat of evaporation of the refrigerant to exchange heat with the object to be cooled, and then returns the low-temperature and low-pressure refrigerant gas to the compressor <NUM>. With this cycle, a refrigeration cycle device for cooling the object to be cooled may be provided.

The compressor <NUM>, the condenser <NUM>, the expander <NUM>, and the evaporator <NUM> are connected through pipes to enable the refrigerant to pass through. The refrigerant passing the compressor <NUM> is in a gaseous state, and the refrigerant passing the expander <NUM> is in a liquid state. The pipes connected to the compressor <NUM> are called gas-side pipes <NUM> and <NUM>, and the pipes connected to the expander <NUM> are called liquid-side pipes <NUM> and <NUM>.

The gas-side pipes <NUM> and <NUM> includes a first gas-side pipe <NUM> connecting the condenser <NUM> to the compressor <NUM> and a second gas-side pipe <NUM> connecting the evaporator <NUM> to the compressor <NUM>. The first gas-side pipe <NUM> may be referred to as a connecting pipe <NUM>. The liquid-side pipes <NUM> and <NUM> includes a first liquid-side pipe <NUM> connecting the condenser <NUM> to the expander <NUM> and a second liquid-side pipe <NUM> connecting the evaporator <NUM> to the condenser <NUM>.

<FIG> illustrates a compressor, according to an embodiment of the disclosure, and <FIG> is a cross-sectional view of the compressor of <FIG>.

Although the compressor will be described based on a rotary compressor for convenience of explanation in the specification, embodiments of the disclosure are not limited to the rotary compressor but may be applied to various other types of compressors.

Referring to <FIG>, the refrigerant discharged from the evaporator <NUM> may pass through an accumulator <NUM> and then flow into the compressor <NUM>. The accumulator <NUM> may be arranged to adjoin the compressor <NUM>, and the accumulator <NUM> and the compressor <NUM> may be connected through a suction tube <NUM>. Furthermore, a discharge tube <NUM> discharging the compressed refrigerant and connected to the condenser <NUM> may be provided on one side of the compressor <NUM>. The suction tube <NUM> may be a refrigerant suction tube <NUM> that sucks the refrigerant into a compression chamber <NUM> and <NUM>.

The accumulator <NUM> may be installed to prevent some of the low-temperature and low-pressure refrigerant discharged from the evaporator <NUM>, which do not reach to a gaseous state but remain in a liquid state, from flowing into the compressor <NUM>. The refrigerant discharged from the evaporator <NUM> flows into the accumulator <NUM> through a connecting tube <NUM>. As the compressor <NUM> has a difficulty in compressing the liquid refrigerant, the compressor <NUM> allows only the gas refrigerant to flow into the compressor <NUM> from the accumulator <NUM>. That is, the liquid refrigerant is left in the accumulator and the gaseous refrigerant flows into the compressor <NUM>.

The low-temperature and low-pressure refrigerant gas flowing into the compressor <NUM> may be compressed in the compressor <NUM> and then discharged into the connection pipe <NUM>. The high-temperature and high-pressure refrigerant gas flowing out of the compressor <NUM> may flow into the condenser <NUM> through the connection pipe <NUM>. The pressure of the refrigerant gas before compression is evaporation pressure, and the pressure of the compressed refrigerant gas flowing into the condenser <NUM> may be referred to as condensing pressure. The condensing pressure is higher than the evaporation pressure.

The compressor <NUM> includes a casing <NUM>, a compression unit <NUM> and a driving unit <NUM> arranged in the casing <NUM>. The driving unit <NUM> may be installed in an upper portion in the casing <NUM> and the compression unit <NUM> may be installed in a lower portion in the casing <NUM>.

The driving unit <NUM> may include a cylindrical stator <NUM> fixed to the inner surface of the casing <NUM>, and a rotator <NUM> rotationally installed within the stator <NUM>. A rotation shaft <NUM> may be press-fitted and coupled to the center of the rotator. When power is applied, the rotator <NUM> and the rotation shaft <NUM> coupled to the rotator <NUM> are rotated, thereby driving the compression unit <NUM>. In this case, the driving unit <NUM> may be operated at various speeds. In other words, the rotator <NUM> may be rotated at various speeds and the compression unit <NUM> may receive the rotation power accordingly.

The compression unit <NUM> may include cylinders <NUM> and <NUM> forming the compression chamber <NUM> and <NUM>, and rolling pistons <NUM> and <NUM> that receive power from the driving unit <NUM> and encircle the compression chamber <NUM> and <NUM>. The cylinders <NUM> and <NUM> may be provided in the plural, and accordingly, a plurality of compression chambers <NUM> and <NUM> separated from each other may be formed. In addition, the compression unit <NUM> may include a plurality of plates <NUM>, <NUM>, and <NUM> covering top and bottom of the plurality of cylinders <NUM> and <NUM> and thus forming the compression chambers <NUM> and <NUM> together.

The plurality of plates <NUM>, <NUM>, and <NUM> may include the first plate <NUM> arranged in an uppermost portion, the second plate <NUM> arranged under the first plate <NUM>, and the third plate <NUM> arranged under the first plate <NUM> and the second plate <NUM>. The second plate <NUM> may be arranged between the first plate <NUM> and the third plate <NUM>.

In <FIG>, shown are the first cylinder <NUM> and the second cylinder <NUM> positioned between the first cylinder <NUM> and the bottom of the casing <NUM>. Accordingly, the first cylinder <NUM> may form the first compression chamber <NUM> and the second cylinder <NUM> may form the second compression chamber <NUM>. The first and second rolling pistons <NUM> and <NUM> may be positioned in the first and second compression chambers <NUM> and <NUM>, respectively. Furthermore, the plates <NUM>, <NUM>, and <NUM> may include the top plate <NUM> arranged above the first cylinder <NUM>, the bottom plate <NUM> arranged under the second cylinder <NUM>, and the middle plate <NUM> located between the first cylinder <NUM> and the second cylinder <NUM>. However, the numbers and shapes of the plurality of cylinders <NUM> and <NUM>, the plurality of compression chambers <NUM> and <NUM>, the plurality of plates <NUM>, <NUM>, and <NUM> are not limited to what are shown in the drawings.

The rotation shaft <NUM> extending from the driving unit <NUM> may be installed by running or passing through the center of the first and second compression chambers <NUM> and <NUM>. The rotation shaft <NUM> may be connected to the first and second rolling pistons <NUM> and <NUM> arranged in the first and second compression chambers <NUM> and <NUM>.

The first and second rolling pistons <NUM> and <NUM> may be coupled to the rotation shaft <NUM>, and may be rotated in the compression chambers <NUM> and <NUM> with eccentricity. With this structure, the first and second rolling pistons <NUM> and <NUM> may be eccentrically rotated in the compression chambers <NUM> and <NUM> and may compress a fluid to be compressed. Furthermore, the first and second rolling pistons <NUM> and <NUM> may be coupled together with eccentricities of different directions. For example, the first and second rolling pistons <NUM> and <NUM> may compress the refrigerant with a phase difference of <NUM> degrees.

The compressor <NUM> including such eccentrically rotating rolling pistons <NUM> and <NUM> is called a rotary compressor.

An oil storage space <NUM> may be provided on the bottom in the casing <NUM> for storing certain oil to be in contact with an end of the rotation axis <NUM>. The oil moves up the rotation axis and flows back down, thereby reducing friction of the compression unit <NUM> or the like.

In order for the compressor <NUM> to operate, the difference between pressure P2 of the internal space <NUM> and pressure P1 of the compression chambers <NUM> and <NUM> should not be excessively large. In other words, when a difference in pressure P2-P1 between the compressor's internal space <NUM> and the compression chambers <NUM> and <NUM> is larger than a pressure difference P2'-P1' at which the compressor is able to operate, compression may not be performed. When a difference in pressure P2-P1 between the compressor's internal space <NUM> and the compression chambers <NUM> and <NUM> is larger than a pressure difference P2'-P1' at which the compressor is able to operate, the driving unit <NUM> may be overloaded because a discharge valve <NUM>, which will be described later, is not opened. That is, when (P2-P1) > (P2'-P1'), the discharge valve <NUM> may not be opened and thus, the driving unit <NUM> may be overloaded.

The compressor <NUM> may include an anti-overload device <NUM> connected to the driving unit <NUM> for preventing a failure of the driving unit <NUM> from overload.

When the anti-overload device <NUM> operates, operation of the refrigeration cycle device <NUM> may be stopped. In other words, the anti-overload device <NUM> may stop the rotation shaft <NUM> of the compressor <NUM> and a motor (not shown) that operates the rotation shaft <NUM>. The anti-overload device <NUM> may be arranged above the casing <NUM>.

When the operation of the compressor <NUM> is stopped, for prompt re-operation of the compressor <NUM>, the compression chambers <NUM> and <NUM> and the internal space <NUM> of the compressor need to be in quick pressure equilibrium. When the stopped state of the compressor <NUM> continues, problems such as oil leaks might occur. Accordingly, the compressor <NUM> needs to be quickly re-operated by making the compression chambers <NUM> and <NUM> with relatively low pressure and the internal space <NUM> with relatively high pressure reach a balanced pressure.

For example, the compressor <NUM> may include the discharge valve <NUM> and a discharge flow path <NUM> for discharging the refrigerant compressed by the compression chambers <NUM> and <NUM>. The discharge valve <NUM> may be arranged on the top of the first plate <NUM>. However, the position of the discharge valve <NUM> is not limited thereto.

When the driving unit <NUM> is operated, the rolling pistons <NUM> and <NUM> may compress the refrigerant gas in the compression chambers <NUM> and <NUM> while making a rotational movement. The discharge valve <NUM> is closed during operation of the compressor <NUM>, and the pressure P2 of the internal space <NUM> may be higher than the pressure P1 in the compression chambers <NUM> and <NUM>. When the refrigerant gas in the compression chambers <NUM> and <NUM> reaches a constant pressure (P1≒P2), the discharge valve <NUM> that has blocked the discharge flow path <NUM> may be opened. In this way, the refrigerant gas may be discharged into the internal space <NUM> of the compressor through the discharge flow path <NUM>. In other words, the discharge valve <NUM> may open the discharge flow path <NUM> for the refrigerant gas of the compression chambers <NUM> and <NUM> to flow into the internal space <NUM>.

On the contrary, when the driving unit <NUM> is abruptly stopped due to various causes, the discharge valve <NUM> may block the discharge flow path <NUM> to prevent backflow of the refrigerant gas. When the discharge flow path <NUM> is blocked, the internal space <NUM> and the compression chambers <NUM> and <NUM> that has been connected to each other are separated and thus, there may be a difference in pressure between the spaces. For example, the internal space <NUM> may have relatively high pressure, and the compression chambers <NUM> and <NUM> may have relatively low pressure.

As an example of the various causes, when the difference between the pressure P1 of the compression chamber and the pressure P2 of the internal space becomes excessively large, the driving unit <NUM> may be overloaded and the anti-overload device <NUM> may be operated. The anti-overload device <NUM> stops the driving unit <NUM> to remove a compression load in the compression unit <NUM>. At this time, the discharge valve <NUM> may block the discharge flow path <NUM>, and there may be a difference in pressure between the internal space <NUM> and the compression chambers <NUM> and <NUM>.

In this case, when the compression load on the driving unit <NUM> is not quickly removed, it might be impossible to re-operate the compressor <NUM>. For example, if the pressure P1 of the compression chamber and the pressure P2 of the internal space do not reach a required pressure equilibrium, the refrigeration cycle device <NUM> may not be re-operated.

However, when a time required for a pressure to be balanced becomes long, the compressor <NUM> and/or the refrigeration cycle device <NUM> including the same may encounter problems such as refrigerant backflow, oil leaks, a decrease in efficiency of the refrigeration cycle device, etc. Therefore, the time required until the balanced pressure is achieved should be reduced or shortened to avoid such problems as refrigerant backflow, oil leaks, a decrease in efficiency of the refrigeration cycle device, etc..

The refrigeration cycle device <NUM> may further include a valve <NUM> for quick arrival at the balanced pressure. The valve <NUM> may make the pressure P2 of the internal space <NUM>, which is relatively high as compared to the pressure of the compression chambers <NUM> and <NUM> because the compressor <NUM> is stopped, closer to the pressure P1 of the compression chambers <NUM> and <NUM>. The valve <NUM> may reduce the time required until the balanced pressure is obtained.

Specifically, as shown in <FIG>, when the internal space <NUM> is in a high pressure state and the compression chambers <NUM> and <NUM> before compression of the refrigeration gas is in a low pressure state, the discharge valve <NUM> may be in a blocked state. Furthermore, the valve <NUM> may be connected to both the internal space <NUM> of the compressor and the external space of the compressor <NUM>. The internal space <NUM> is a relatively high pressure space in which a compressed refrigerant gas is present, and the external space of the compressor <NUM> is a relatively low pressure space in which a refrigerant gas before compression is present. The valve <NUM> may connect the internal space <NUM> of the compressor on a high pressure side, to the external space of the compressor on a low pressure side. In this way, the refrigerant gas may be discharged from the internal space <NUM> to the external space of the compressor through the valve <NUM>. The valve <NUM> and the external space may be connected through a bypass outlet tube 101b. The bypass outlet tube 101b may be connected to the connection tube <NUM>. The refrigerant flowing to the connection tube <NUM> through the bypass outlet tube 101b may flow back to the compressor <NUM> through the accumulator <NUM>.

Pressure of the external space of the compressor may be equal or similar to the pressure of the compression chambers <NUM> and <NUM> before compression of the refrigerant gas. That is, it may be a space with a lower pressure than in the internal space <NUM>. For example, the external space of the compressor may be the connection tube <NUM>. It is not, however, limited thereto, and the external space of the compressor may be a second gas-side pipe <NUM>, the accumulator <NUM>, or the suction tube <NUM>. In other words, it is also possible that the bypass outlet tube 101b is connected to the second gas-side pipe <NUM>, the accumulator <NUM>, or the suction tube <NUM>.

Although in <FIG> the valve <NUM> is shown as being connected to the external space through the bypass outlet tube 101b, it is not limited thereto, but the valve <NUM> may be directly connected to the external space depending on the position of the valve <NUM> or the valve <NUM> itself may be arranged outside the casing <NUM>. Furthermore, a bypass inlet <NUM>, which will be described later, may be connected to the internal space <NUM> directly or through an extra pipe, so that a high pressure refrigerant gas flows into the valve <NUM>.

Moreover, the valve <NUM> may serve to prevent backflow of the refrigerant toward the internal space <NUM> from the outside of the compressor <NUM> when the compressor <NUM> is stopped. That is, it may prevent the refrigerant from flowing backward from the side of the condenser <NUM> to the side of the compressor <NUM>. In an embodiment of the disclosure, the valve <NUM> may solely block the back-flowing refrigerant without an extra check valve and a solenoid valve and facilitate the pressure P1 of the compression chambers <NUM> and <NUM> and the pressure P2 of the internal space <NUM> to quickly reach a balanced pressure, thereby saving compressor manufacturing costs and material costs. Motion of the valve <NUM> will be described later in detail.

Although the valve <NUM> is shown in the casing <NUM> in <FIG>, it is not limited thereto, and it may be arranged in various positions in which to facilitate quick arrival at the balanced pressure and prevent backflow of the refrigerant. For example, it is also possible to arrange the valve <NUM> on the outside of the casing <NUM>. For example, the valve <NUM> may be arranged at the connection pipe <NUM>.

<FIG> illustrates a valve during operation of the compressor <NUM> of <FIG>. <FIG> is an exploded view of the valve of <FIG>. <FIG> is a cross-sectional view of a valve during operation of the compressor <NUM> of <FIG>.

Referring to <FIG>, the valve <NUM> may include a plurality of valve cases <NUM>, <NUM> and <NUM> that constitute the exterior. The valve cases <NUM>, <NUM> and <NUM> may include the first case <NUM>, the second case <NUM>, and the third case <NUM>. The first case <NUM> may be an upper case <NUM>, the second case <NUM> may be a middle case <NUM>, and the third case <NUM> may be a lower case <NUM>. In other words, the first case <NUM> may form the external appearance of an upper portion of the valve <NUM>, the second case <NUM> may form the external appearance of a middle portion of the valve <NUM>, and the third case <NUM> may form the external appearance of a lower portion of the valve <NUM>. Although the plurality of valve cases <NUM>, <NUM> and <NUM> are separately formed in <FIG>, they are not limited thereto and may be integrated into a single body.

The plurality of valve cases <NUM>, <NUM> and <NUM> may have a cylindrical shape. However, the shape of the plurality of valve cases <NUM>, <NUM> and <NUM> is not limited thereto and may have various forms.

The refrigerant outlet <NUM>, the refrigerant outlet tube 101a, and the bypass outlet tube 101b may be formed at the first case <NUM>. The refrigerant outlet tube 101a and the bypass outlet tube 101b may extend vertically. Furthermore, the refrigerant outlet tube 101a and the bypass outlet tube 101b may be formed in a cylindrical shape. It is not, however, limited thereto, and they may be formed in other various shapes that allow the refrigerant to flow. The refrigerant outlet <NUM> may allow the refrigerant gas to be discharged from the side of the internal space <NUM> to the side of the condenser <NUM>.

The second case <NUM> may receive a sealing member <NUM> and a floating body <NUM>. The second case <NUM> may be arranged between the first case <NUM> and the third case <NUM> in the vertical direction. It is not, however, limited thereto, and at least one of the first case <NUM> or the second case <NUM> may be omitted, or it may be arranged between the first case <NUM> and the second case <NUM> in the left-right direction.

The second case <NUM> may include multiple portions. The multiple portions may include a first portion 102a, a second portion 102b, a third portion 102c, and a fourth portion 102d. The first portion 102a may be a portion to be coupled to the first case <NUM>. The second portion 102b may connect between the first portion 102a and the third portion 102c. The second portion 102b may be a slanting (slanted) portion 102b. The third portion 102c may connect between the second portion 102b and the fourth portion 102d. In the fourth portion 102d, the floating body <NUM>, the sealing member <NUM>, and an elastic member <NUM>, which will be described later, may be arranged. The fourth portion 102d may have the largest area of the multiple portions.

The slanting portion 102b may be slanted upward toward the first case <NUM> to guide the refrigerant to flow from the refrigerant inlet <NUM> to the refrigerant outlet <NUM>. In other words, the slanting portion 102b may have a smaller cross-sectional area toward the first portion 102a from the third portion 102c.

In the second case <NUM>, a bypass inlet <NUM> and a connection flow path <NUM> may be formed.

The third case <NUM> may include a bottom wall 103a, an extension wall 103b, and a base 103c. The refrigerant inlet <NUM> may be formed at the bottom wall 103a. The refrigerant inlet <NUM> may be formed between the bottom wall 103a and the extension wall 103b. The refrigerant inlet <NUM> may be separated from each other and provided as a plurality of refrigerant inlets <NUM>, for example, with the bottom wall 103a disposed between adjacent refrigerant inlets <NUM>. It is not, however, limited thereto, and the plurality of refrigerant inlets <NUM> may be connected to form a single refrigerant inlet <NUM>. The extension wall 103b may protrude upward from the base 103c. The base 103c may be arranged at the lowest portion of the third case <NUM>. The base 103c may support the first case <NUM> and the second case <NUM>. The refrigerant inlet <NUM> may allow the refrigerant gas to flow in from the internal space <NUM> or from the side of the accumulator <NUM>.

The valve cases <NUM>, <NUM> and <NUM> may form the valve chamber <NUM>. A main flow path <NUM> may be formed in the valve chamber <NUM>. However, the valve chamber <NUM> may be formed not only by the valve cases <NUM>, <NUM> and <NUM> but also by components in the compressor <NUM>. It is now assumed that there are the valve cases <NUM>, <NUM> and <NUM>, for convenience of explanation.

The valve <NUM> may include the main flow path <NUM> in which the refrigerant flows. The main flow path <NUM> may be formed inside the valve cases <NUM>, <NUM> and <NUM>. In other words, the main flow path <NUM> may be formed in the valve chamber <NUM>. The main flow path <NUM> may include the refrigerant inlet <NUM> and the refrigerant outlet <NUM>. During operation of the compressor <NUM>, the refrigerant flowing in from the refrigerant inlet <NUM> may pass through the valve chamber <NUM> and flow out through the refrigerant outlet <NUM>. In the valve <NUM>, the refrigerant inlet <NUM> may be connected to the internal space <NUM> to discharge the refrigerant from the internal space <NUM> with high pressure to an external space of the compressor <NUM> with low pressure, and the refrigerant outlet <NUM> may be connected to the outside of the casing <NUM> through the refrigerant outlet tube 101a. Specifically, the refrigerant outlet <NUM> may be connected to the connection tube <NUM> or the suction tube <NUM>. It is not, however, limited thereto, and the refrigerant outlet <NUM> may be connected to anywhere in a low pressure area or space.

The main flow path <NUM> may include a first main flow path <NUM> and a second main flow path <NUM>. The first main flow path <NUM> may be formed in an area corresponding to the first portion 102a, the second portion 102b, and the third portion 102c. The second main flow path <NUM> may be formed in an area corresponding to the fourth portion 102d. The first main flow path <NUM> and the second main flow path <NUM> may be internal flow path <NUM> formed in the valve chamber <NUM>.

The valve <NUM> may include the floating body <NUM> and the sealing member <NUM>.

The floating body <NUM> may be arranged in the valve chamber <NUM>. Specifically, the floating body <NUM> may be arranged in the second case <NUM>. The floating body <NUM> may be arranged in the fourth portion 102d and may move up or down. As the refrigerant flows in a direction from the third case at which the refrigerant inlet <NUM> is formed to the first case <NUM> at which the refrigerant outlet <NUM> is formed during operation of the compressor <NUM>, the floating body <NUM> may be arranged in an upper part of the fourth portion 102d. In this case, the floating body <NUM> may block the bypass flow path <NUM>. Accordingly, the refrigerant gas flowing through the bypass flow path <NUM> may not be present.

The floating body <NUM> may include a bypass groove <NUM> and a sealing member groove <NUM>.

The bypass groove <NUM> may be formed by being sunken or recessed along the circumferential surface of the floating body <NUM> to form the bypass flow path <NUM>. However, the form of the bypass groove <NUM> is not limited thereto, and may have various forms. The bypass groove <NUM> may be formed between grooves <NUM> of the plurality of sealing members 140a, 140b and 140c. The position of the bypass groove <NUM> is not, however, limited thereto.

The sealing member grooves <NUM> may be formed by being sunken or recessed along the circumferential surface of the floating body <NUM> for the sealing member <NUM> to be inserted thereto. However, the form of the bypass groove <NUM> is not limited thereto, and may have various forms. The sealing member grooves <NUM> may be formed above and below the bypass groove <NUM>. It is not, however, limited thereto, and may be formed only above or only below the bypass groove <NUM>.

Although the floating body <NUM> is shown as having a cylindrical shape, it is not limited thereto and may have various shapes.

The sealing member <NUM> may prevent the refrigerant from flowing to the bypass flow path <NUM> during operation of the compressor <NUM>. In other words, to prevent the refrigerant from leaking out into the bypass flow path <NUM> while the refrigerant flows in the main flow path <NUM>, the sealing member <NUM> may be provided in the valve cases <NUM>, <NUM> and <NUM>. As the refrigerant does not leak out from the main flow path <NUM>, the compression power may increase and an amount of the refrigerant flowing into the compressor casing <NUM> may be minimized.

The sealing member <NUM> may be provided as a plurality of sealing members <NUM>. The sealing members <NUM> may be arranged to correspond to the positions of the sealing member grooves <NUM>. Although the sealing members <NUM> are shown as being positioned above and below the bypass inlet <NUM> and the bypass outlet <NUM>, they are not limited thereto and may be arranged in various positions in which to prevent the refrigerant from leaking out. The sealing member <NUM> may be formed of Teflon, for example.

The valve <NUM> may include the bypass flow path <NUM> to which the refrigerant is detoured or redirected. The bypass flow path <NUM> may be formed between the valve cases <NUM>, <NUM> and <NUM> and the floating body <NUM>. The bypass flow path <NUM> may be formed between the valve chamber <NUM> and the floating body <NUM>.

The valve <NUM> may further include a connection flow path <NUM>. Specifically, the bypass flow path <NUM> may include the connection flow path <NUM>. The connection flow path <NUM> may be arranged between the bypass outlet <NUM> and the bypass outlet tube 101b. Specifically, in the bypass flow path <NUM>, the connection flow path <NUM> may be arranged on a downstream side of the bypass outlet <NUM>.

Referring to <FIG>, a function of the valve <NUM> during operation of the compressor <NUM> will be described.

While the compressor <NUM> is operated, the refrigerant gas may be discharged from the compression chambers <NUM> and <NUM> into the internal space <NUM> through the discharge valve <NUM> and may then flow from the compressor <NUM> to the condenser <NUM>. The valve <NUM> may be arranged between the compressor <NUM> and the condenser <NUM>. Accordingly, the refrigerant may flow into the valve chamber <NUM> through the refrigerant inlet <NUM> of the valve <NUM> and may be discharged out of the valve <NUM> through the refrigerant outlet <NUM>.

In this case, the refrigerant gas flowing past the valve chamber <NUM> to the condenser <NUM> may pressurize the floating body <NUM> upward so that the floating body <NUM> may be moved upward. The floating body <NUM> may come into contact with the top of the fourth portion 102d. As the floating body <NUM> is moved upward, it may force open the main flow path <NUM>. Furthermore, when the floating body <NUM> is moved upward, the bypass inlet <NUM> and the bypass outlet <NUM> may not be connected to the bypass grooves <NUM>. That is, the bypass flow path <NUM> may be blocked.

<FIG> illustrates a valve when the compressor of <FIG> is stopped. <FIG> is a cross-sectional view of a valve when the compressor of <FIG> is stopped.

Referring to <FIG> and <FIG>, when the compressor <NUM> is stopped, the floating body <NUM> may be moved downward because the side of the condenser <NUM> has higher pressure than on the side of the compressor <NUM>. Specifically, when the compressor <NUM> is stopped, compression of the refrigerant gas may be prevented, and the refrigerant gas may flow backward because the side of the condenser has higher pressure than on the side of the compressor <NUM>. Accordingly, the refrigerant gas may pressurize the floating body <NUM> downward. Specifically, the floating body <NUM> may be moved down in the valve chamber <NUM> and may contact the bottom wall 103a. The floating body <NUM> may move down and block the refrigerant inlet <NUM>. This is because the driving unit <NUM> and the compression unit <NUM> may be operated during operation of the compressor <NUM> so that the refrigerant gas flows to the condenser <NUM> on the high pressure side, but when the compressor <NUM> is stopped, the driving unit <NUM> and the compression unit <NUM> are stopped so the compressor <NUM> may not make the refrigerant flow to the condenser <NUM>.

In other words, when the compressor <NUM> is stopped, the refrigerant may flow to the compressor <NUM> from the condenser <NUM> because the side of the condenser <NUM> has relatively higher pressure than on the side of the compressor <NUM> and there is no power to send it to the condenser <NUM> from the compressor <NUM>. That is, the refrigerant may flow backward from the side of the condenser <NUM> with high pressure to the side of the compressor <NUM> with low pressure. The refrigerant may flow backward from the side of the refrigerant outlet <NUM> to the side of the refrigerant inlet <NUM>.

Accordingly, the back-flowing refrigerant may pressurize the floating body <NUM> so that the floating body <NUM> is moved from the side of the condenser <NUM> to the side of (toward) the compressor <NUM>. The floating body <NUM> pressurized by the back-flowing refrigerant may move to the side of the refrigerant inlet <NUM> and block the refrigerant inlet <NUM>. For example, the floating body <NUM> may come into contact with the bottom wall 103a of the bottom case. Finally, when the compressor <NUM> is stopped, the floating body <NUM> may block the main flow path <NUM>, thereby preventing the refrigerant from flowing backward into the compressor <NUM>. The floating body <NUM> may be moved from an upper portion to a lower portion in the valve chamber <NUM>.

As described above, when the compressor <NUM> is abruptly stopped, problems such as refrigerant backflow, oil leaks, a decrease in efficiency of the refrigeration cycle device, etc., may occur. Hence, the internal space <NUM> of the compressor and the compression chambers <NUM> and <NUM> quickly reach a pressure equilibrium so that the compressor <NUM> can be re-operated.

The floating body <NUM> may block the main flow path <NUM> and open the bypass flow path <NUM>.

The bypass flow path <NUM> may include the bypass inlet <NUM>, the bypass outlet <NUM>, and a middle bypass flow path <NUM>.

When the compressor <NUM> is stopped, the floating body <NUM> is moved downward to block the refrigerant inlet <NUM>, so the floating body <NUM> may block the main flow path <NUM>. Furthermore, as the bypass groove <NUM> is connected to the bypass inlet <NUM> and the bypass outlet <NUM>, the middle bypass flow path <NUM> may be connected to the bypass inlet <NUM> and the bypass outlet <NUM>. In other words, as the refrigerant flows backward, the floating body <NUM> may be moved down to open the bypass inlet <NUM> and the bypass outlet <NUM>.

In this case, as the refrigerant pressure P2 of the internal space <NUM> of the compressor is higher than the refrigerant pressure P1 of the compression chamber, the discharge valve <NUM> may be in a closed state. Hence, in order for the internal space <NUM> of the compressor and the compression chambers <NUM> and <NUM> to reach the pressure equilibrium, the refrigerant gas of the internal space <NUM> with relatively high pressure may flow into the valve chamber <NUM> through the bypass inlet <NUM> and then flow to the bypass outlet <NUM> through the middle bypass flow path <NUM>. The refrigerant flowing out from the bypass outlet <NUM> may flow out to an external space of the compressor with relatively low pressure from the bypass outlet tube 101b through the connection flow path <NUM>.

The pressure of the external space of the compressor may be equal or similar to the pressure of the compression chambers <NUM> and <NUM> before compression of the refrigerant gas. That is, it may be a space with a lower pressure than in the internal space <NUM>. For example, the external space of the compressor may be the connection tube <NUM>. It is not, however, limited thereto, and the external space of the compressor may be the second gas-side pipe <NUM>, the accumulator <NUM>, or the suction tube <NUM>. In other words, it is also possible that the bypass outlet <NUM> is connected to the second gas-side pipe <NUM>, the accumulator <NUM>, or the suction tube <NUM>.

However, the connection flow path <NUM> may be omitted. For example, the refrigerant gas may sequentially pass the bypass inlet <NUM>, the middle bypass flow path <NUM>, and the bypass outlet <NUM> and may be discharged directly to the outside without the connection flow path <NUM>.

The bypass inlet <NUM> may be connected to the internal space <NUM> of the casing <NUM>. Specifically, the bypass inlet <NUM> may be connected to the internal space <NUM> to make the high pressure of the internal space <NUM> reach a balanced pressure. However, it is not necessary for the valve <NUM> to be arranged in the casing <NUM>, and even when the valve <NUM> is arranged on the outside, it may be connected through an extra pipe (not shown) for connecting between the internal space <NUM> and the bypass inlet <NUM>.

The valve <NUM> may be arranged in various positions without positional limitations, thereby increasing space utilization of the compressor <NUM> and the refrigeration cycle device.

The bypass inlet <NUM> may be connected to the internal space <NUM> with relatively high pressure, and the bypass outlet <NUM> may be connected to the external space of the compressor <NUM> with relatively low pressure.

In other words, when the main flow path <NUM> is blocked due to movement of the floating body <NUM>, the refrigerant in the internal space <NUM> may flow into the valve chamber <NUM> through the bypass inlet <NUM>. The refrigerant in the valve chamber <NUM> may be linked to an external space through the bypass outlet <NUM> and the bypass outlet tube 101b. In other words, the refrigerant may flow to the connection tube <NUM> through the bypass outlet <NUM> and the bypass outlet tube 101b (see <FIG>). Accordingly, the refrigerant that has flowed to the connection tube <NUM> may flow back to the accumulator <NUM>. Among the refrigerant passing the accumulator <NUM>, some refrigerant in a liquid state may stay in the accumulator <NUM> and only gaseous refrigerant may flow back into the compressor <NUM>. The accumulator <NUM> may be arranged to adjoin the compressor <NUM>, and the accumulator <NUM> and the compressor <NUM> may be connected through the suction tube <NUM>. Accordingly, the refrigerant gas may flow back into the compressor <NUM> through the suction tube <NUM>. The suction tube <NUM> may be connected to the compression chambers <NUM> and <NUM> to suck in the refrigerant.

For example, when the main flow path <NUM> is blocked and the bypass flow path <NUM> is opened, the internal space <NUM> and the compression chambers <NUM> and <NUM> may be connected through the bypass flow path <NUM>, the connection tube <NUM>, the accumulator <NUM> and the suction tube <NUM> even though the discharge valve <NUM> has blocked the discharge flow path <NUM>.

Accordingly, the refrigerant that has been in the internal space <NUM> flows into the connection tube <NUM> and may pass through the accumulator <NUM> again and flow to the suction tube <NUM>. The refrigerant gas that has flowed to the suction tube <NUM> flows to the compression chambers <NUM> and <NUM>, so the internal space <NUM> and the compression chambers <NUM> and <NUM> may reach a balanced pressure without opening the discharge valve <NUM>. In other words, the pressure P2 of the internal space <NUM> may be forced to be dropped down to be close to the pressure P1 of the compression chambers <NUM> and <NUM>.

In the above process, a difference in pressure P2-P1 between the compression chambers <NUM> and <NUM> of the compressor and the internal space <NUM> may be smaller than pressure P2'-P1' at which operation is possible. That is, (P2'-P1') > (P2-P1). As a result, the compressor <NUM> may be re-operated.

The balanced pressure may be close to the pressure P1 of the compression chambers <NUM> and <NUM>. The level of the balanced pressure is not, however, limited thereto.

In this way, the valve <NUM> according to an embodiment of the disclosure may make the pressure of the internal space <NUM> of the compressor reach a balanced pressure with the pressure of the compression chambers <NUM> and <NUM> and the accumulator <NUM> without an extra check valve and solenoid valve, so that the compressor may be re-operated as soon as possible. Accordingly, production costs and material costs for the refrigeration cycle device may be saved.

Once again, the compressor may be abruptly stopped due to various causes such as external electric shocks, excessive internal refrigerant intake flow rates, pressure pulsations in the cycle, etc. For example, when the pressure difference P2-P1 is greater than a pressure difference P2'-P1' at which the cycle allows operation of the compressor, because the compressor pressure P1 is too low or the pressure P2 of the internal space is too high, the discharge valve <NUM> may not open the discharge flow path <NUM> and instead the anti-overload device <NUM> may be operated to stop the driving unit <NUM>.

As the compressor <NUM> is stopped, the refrigerant may flow backward into the compressor <NUM> from the condenser <NUM>, in which case the floating body <NUM> of the valve <NUM> may be moved downward due to the pressure from the refrigerant backflow, blocking the refrigerant inlet <NUM> and thus preventing the backflow of the refrigerant.

In this case, the floating body <NUM> may open the bypass flow path <NUM>. The bypass inlet <NUM> may be connected to the internal space <NUM> of the compressor directly or through an extra pipe (not shown). The bypass outlet <NUM> may be connected to the external space of the compressor directly or through the connection flow path <NUM> and the bypass outlet tube 101b.

Accordingly, due to the pressure difference, the refrigerant gas may flow from the internal space <NUM> on a relatively high-pressure side to the external space on a relatively low-pressure side. This may make the pressure P2 of the internal space and the pressure P1 of the compression chamber reach a balanced pressure within a short time, and the difference in pressure P2-P1 between the internal space and the compression chamber becomes smaller than the pressure difference P2'-P1' at which the compressor may be operated, thereby re-operating the compressor <NUM> and the refrigeration cycle device <NUM>.

<FIG> is a cross-sectional view of a valve when a compressor is stopped, according to an embodiment of the disclosure.

The same features as in the aforementioned embodiment are denoted by the same reference numerals, and the overlapping description will not be repeated.

Referring to <FIG>, the valve <NUM> may further include an elastic member <NUM>. The elastic member <NUM> may pressurize the floating body <NUM> so that the floating body <NUM> is able to quickly block the refrigerant inlet <NUM> when the compressor <NUM> is stopped. In other words, the elastic member <NUM> may allow the main flow path <NUM> to be quickly blocked and the bypass flow path <NUM> to be opened.

The elastic member <NUM> may be arranged between the refrigerant outlet <NUM> and the floating body <NUM>. For example, it may be arranged in the fourth portion 102d of the second case <NUM>. The position of the elastic member <NUM> is not, however, limited thereto, and the elastic member <NUM> may be arranged in various positions in which the floating body <NUM> is able to quickly block the refrigerant inlet <NUM> when the compressor <NUM> is stopped.

<FIG> is a schematic cross-sectional view of a valve during operation of a compressor, according to an embodiment of the disclosure. <FIG> is a schematic cross-sectional view of the valve when the compressor of <FIG> is stopped.

Referring to <FIG> and <FIG>, the valve <NUM> may further include a fixed body <NUM>. The fixed body <NUM> may be fixed in the valve case <NUM>.

The fixed body <NUM> may include a plurality of fixed body inlets <NUM> and a plurality of fixed body outlets <NUM>. The plurality of fixed body inlets <NUM> may include a first fixed body inlet 171a and a second fixed body inlet 171b. The fixed body inlet <NUM> may be the refrigerant inlet <NUM>. The plurality of fixed body outlets <NUM> may include a first fixed body outlet 172a and a second fixed body outlet 172b. The refrigerant that has flowed in through the plurality of fixed body inlets <NUM> may flow out to the refrigerant outlet <NUM> through the plurality of fixed body outlets <NUM>.

The first fixed body inlet 171a and outlet 172a are shown as being larger than the second fixed body inlet 171b and outlet 172b in <FIG>. For example, the width of the second fixed body inlet 171b may correspond to the distance "b" in <FIG> and the width of the second fixed body outlet 172b is denoted by the distance "B" in <FIG>. Thus, the second fixed body inlet 171b and the second fixed body outlet 172b may have different widths, with B being greater than b. For example, the width of the first fixed body inlet 171a and the width of the first fixed body outlet 172a may be the same as each other, and each may be greater than the distance B. However, the disclosure is not limited to these example widths. Furthermore, the fixed body inlet <NUM> and the fixed body outlet <NUM> may each be formed as singular inlet / outlet, respectively, rather than a plurality of inlets / outlets, respectively.

The floating body <NUM> may be provided as a plurality of floating bodies. For example, the plurality of floating bodies <NUM> may include a first floating body <NUM> and a second floating body <NUM>.

The first floating body <NUM> may be arranged on the top of (above) the fixed body <NUM>. In other words, the first floating body <NUM> may be arranged on the top of (above) the plurality of fixed body inlets <NUM>. Accordingly, in an example the floating body <NUM> may also be provided as a plurality of floating bodies <NUM>. The first floating body <NUM> may be located on the top of (above) the fixed body inlet <NUM> to open or block the main flow path <NUM>. Accordingly, during operation of the compressor <NUM>, the first floating body <NUM> may open the fixed body outlet <NUM>, and when the compressor <NUM> is stopped, the first floating body <NUM> may block the fixed body outlet <NUM> to prevent refrigerant backflow. For example, the back-flowing refrigerant may pressurize the first floating body <NUM> so that the first floating body <NUM> is moved from the side of the condenser <NUM> to the side of (toward) the compressor <NUM>. The first floating body <NUM> pressurized by the back-flowing refrigerant may move to the side of (toward) the fixed body outlet <NUM> to block the fixed body outlet <NUM>. For example, the first floating body <NUM> may come into contact with an upper portion of the fixed body <NUM> so as to block the fixed body outlet <NUM>.

The second floating body <NUM> may be arranged in a space in the fixed body <NUM>. The second floating body <NUM> may be arranged in the fixed body <NUM> to open or block the bypass flow path <NUM>. Accordingly, the second floating body <NUM> may open or block the bypass flow path <NUM>. For example, the second floating body <NUM> may block the bypass outlet <NUM> during operation of the compressor <NUM> and may open the bypass outlet <NUM> when the compressor <NUM> is stopped. For example, the second floating body <NUM> may come into contact with a bottom portion of the fixed body <NUM> so as to open the bypass outlet <NUM>. Accordingly, the internal space <NUM> may quickly reach a balanced pressure.

Each of the plurality of floating bodies <NUM> may include a hollow portion. That is, the first floating body <NUM> may include a first floating body hollow portion 121a, and the second floating body <NUM> may include a second floating body hollow portion 122a.

The first floating body hollow portion 121a may be formed to be smaller than the refrigerant outlet <NUM>, and the second floating body hollow portion 122a may be formed to be smaller than the refrigerant inlet <NUM>. As shown in <FIG>, the refrigerant outlet <NUM> may have a width corresponding to a distance "A. " The opening or first floating body hollow portion 121a provided in the first floating body <NUM> may have a width (e.g., a diameter) corresponding to a distance "a. " For example, the distance "A" may be greater than the distance "a. " As shown in <FIG>, the opening or second floating body hollow portion 122a provided in the second floating body <NUM> may have a width (e.g., a diameter) corresponding to a distance "b. " For example, the width of the second fixed body outlet 172b is denoted by the distance "B" in <FIG>, and the distance "B" is greater than the distance "b.

In an embodiment of the disclosure, the fixed body inlet <NUM> may be the refrigerant inlet <NUM>. For example, the first fixed body inlet 171a and the second fixed body inlet 171b may be the refrigerant inlet <NUM>. In an embodiment of the disclosure, the main flow path <NUM> includes the fixed body inlet <NUM>, the fixed body outlet <NUM>, a first branch flow path 154a, a second branch flow path 154b, and a merging flow path <NUM> and the refrigerant outlet <NUM> may be included. Referring to <FIG>, the refrigerant flowing into the fixed body inlet <NUM> may pass through the first branch flow path 154a or the second branch flow path 154b and merge in the merging flow path <NUM>. The refrigerant passing through the merging passage <NUM> may flow to the outside of the valve chamber <NUM> through the refrigerant outlet <NUM>.

In an embodiment of the disclosure, the bypass flow path <NUM> may include the second fixed body inlet 171b, the second branch flow path 154b, and the bypass outlet <NUM>. The second fixed body inlet 171b may be the bypass inlet <NUM>. Referring to <FIG>, the refrigerant flowing into the second fixed body inlet 171b may flow to the outside of the valve chamber <NUM> through the bypass outlet <NUM> through the second branch flow path 154b.

Referring to <FIG>, the floating body <NUM> may include a plurality of bodies 120a and 120b. The plurality of bodies 120a and 120b may include a first body 120a and a second body 120b. The plurality of bodies 120a and 120b may be integrally formed. They are not, however, limited thereto, and may also be formed separately.

The first body 120a may be arranged on one side in the valve chamber <NUM>, and the second body 120b may be arranged on the other side in the valve chamber <NUM>. For example, where the valve chamber <NUM> is cylindrically shaped, the first body 120a may be disposed on one radial side of the valve chamber <NUM>, and the second body 120b may be disposed on the other radial side of the valve chamber <NUM>. The bypass flow path <NUM> may be formed between the first body 120a and a wall of the valve chamber <NUM>. In other words, the bypass flow path <NUM> may be formed between the first body 120a and the valve case <NUM>. It is not, however, limited thereto, and may also be formed between the second body 120b and the valve case <NUM>. The first body 120a may open or block the refrigerant inlet <NUM>. Accordingly, a flow of the refrigerant in the valve chamber <NUM> may be controlled by the first body 120a opening the refrigerant inlet <NUM> when the compressor <NUM> is operated and blocking the refrigerant inlet <NUM> when the compressor <NUM> is stopped. For example, the back-flowing refrigerant may pressurize the first body 120a so that the first body 120a is moved from the side of the condenser <NUM> to the side of (toward) the compressor <NUM>. The first body 120a pressurized by the back-flowing refrigerant may move to the side of (toward) the refrigerant inlet <NUM> to block the refrigerant inlet <NUM>.

As the first body 120a is moved down in the valve chamber <NUM>, the first body 120a may open the bypass flow path <NUM>. The first body 120a may open the bypass inlet <NUM> and the bypass outlet <NUM> so that the refrigerant in the compressor casing <NUM> may flow out of the casing <NUM> through the middle bypass flow path <NUM>. In this case, the bypass inlet <NUM> may be connected to the inside of the casing <NUM>, and the bypass outlet <NUM> may be connected to the outside of the casing <NUM>. Although the connection may be made directly, the connection may also be made through an extra connection tube or the like.

The valve <NUM> may further include a sealing member <NUM>. The sealing member <NUM> may include a plurality of sealing parts 140a, 140b, and 140c. The plurality of sealing parts 140a, 140b, and 140c may include a first sealing part 140a, a second sealing part 140b, and a third sealing part 140c. Of the plurality of sealing parts 140a, 140b and 140c, the first sealing part 140a may be arranged in an uppermost portion in the valve chamber <NUM>. The second sealing part 140b may be connected to the first sealing part 140a and may extend vertically (e.g., in an axial direction of the valve chamber <NUM>. The third sealing part 140c may be connected to the second sealing part 140b. Of the plurality of sealing parts 140a, 140b and 140c, the third sealing part 140c may be arranged in a lowermost portion in the valve chamber <NUM>. The sealing member <NUM> may be arranged between the valve case <NUM> and the first body 120a. The sealing member <NUM> may be arranged in an area where the bypass flow path <NUM> is formed. In this way, the sealing member <NUM> may prevent the refrigerant from leaking out of the bypass flow path <NUM> when the compressor <NUM> is stopped. For example, the sealing member <NUM> may prevent the refrigerant from leaking into the main flow path <NUM> from the middle bypass flow path <NUM> when the compressor <NUM> is stopped.

The bypass inlet <NUM> may be arranged in a lower portion and the bypass outlet <NUM> may be arranged in an upper portion. The positions of the bypass inlet <NUM> and bypass outlet <NUM> are not, however, limited thereto.

Referring to <FIG>, the refrigerant introduced into the valve chamber <NUM> through the refrigerant inlet <NUM> may pass through an internal flow path <NUM> formed inside the valve chamber <NUM> and through the refrigerant outlet <NUM> flow to the outside of the valve chamber <NUM>.

Referring to <FIG>, the refrigerant introduced into the valve chamber <NUM> through the bypass inlet <NUM> may pass through the middle bypass flow path <NUM> and flows out of the valve chamber <NUM> through the bypass outlet <NUM>.

Referring to <FIG> and <FIG>, the valve <NUM> may further include an upper guard wall <NUM>, a lower guard wall <NUM>, and a guide wall <NUM>. For example, the valve case <NUM> may further include the upper guard wall <NUM>, the lower guard wall <NUM>, and the guide wall <NUM>.

The upper guard wall <NUM> may be formed on the top of (above) the first floating body <NUM> to prevent the first floating body <NUM> from falling out of the valve case <NUM>. The upper guard wall <NUM> may form the refrigerant outlet <NUM>. For example, when the compressor <NUM> is stopped the back-flowing refrigerant may pressurize the first floating body <NUM> so that the first floating body <NUM> is moved from the side of the condenser <NUM> to the side of (toward) the compressor <NUM>. The first floating body <NUM> pressurized by the back-flowing refrigerant may be moved downward (toward refrigerant inlet <NUM>) in the valve chamber <NUM> to block the main flow path <NUM>. For example, the first floating body <NUM> may move downward until the first floating body <NUM> comes into contact with an upper portion of fixed body <NUM> to block the main flow path <NUM>.

The lower guard wall <NUM> may be formed underneath (below) the second floating body <NUM> to prevent the second floating body <NUM> from falling out of the valve case <NUM>. The lower guard wall <NUM> may form the refrigerant inlet <NUM>.

The guide wall <NUM> may be formed to be slanted upward to guide the second floating body <NUM> and the flow of the refrigerant. In the guide wall <NUM>, the bypass inlet <NUM> and the bypass outlet <NUM> may be formed.

The second floating body <NUM> may be formed in a shape corresponding to the guide wall <NUM>. That is, the second floating body <NUM> may be formed to be slanted upward. The second floating body <NUM> may open or block the bypass flow path <NUM>. The second floating body <NUM> may open or block both the bypass inlet <NUM> and the bypass outlet <NUM>. For example, as the second floating body <NUM> is moved down in the valve chamber <NUM>, the second floating body <NUM> may open the bypass flow path <NUM>. The second floating body <NUM> may open the bypass inlet <NUM> and the bypass outlet <NUM> so that the refrigerant in the compressor casing <NUM> may flow out of the casing <NUM> through the middle bypass flow path <NUM>. In this case, the bypass inlet <NUM> may be connected to the inside of the casing <NUM>, and the bypass outlet <NUM> may be connected to the outside of the casing <NUM>. Although the connection may be made directly, the connection may also be made through an extra connection tube or the like.

Referring to <FIG> , the refrigerant introduced through the refrigerant inlet <NUM> may pass through the first main passage <NUM> , the second main passage <NUM> , and the refrigerant outlet <NUM> in order to flow to the outside of the valve chamber <NUM>.

<FIG> is a cross-sectional view of a compressor, according to an embodiment of the disclosure. <FIG> is a schematic cross-sectional view of the valve during operation of the compressor of <FIG>. <FIG> is a schematic cross-sectional view of the valve when the compressor of <FIG> is stopped.

Referring to <FIG>, the discharge tube <NUM> may be provided as a plurality of discharge tubes. The plurality of discharge tubes may include a first discharge tube 12a and a second discharge tube 12b.

The high-pressure refrigerant present in the internal space <NUM> of the compressor may flow to the condenser through the first discharge tube 12a and the second discharge tube 12b.

The valve <NUM> may be formed in a plate. For example, the valve chamber <NUM> of the valve <NUM> may be formed without an extra case. Accordingly, material costs and production costs may be saved.

The compressor <NUM> may include the compression chambers <NUM> and <NUM> for compressing the refrigerant, and the refrigerant suction tube <NUM> for sucking the refrigerant into the compression chambers <NUM> and <NUM>.

The valve <NUM> may be arranged between the internal space <NUM> and the refrigerant suction tube <NUM> so that the bypass flow path <NUM> discharges the refrigerant from the internal space <NUM> to the refrigerant suction tube <NUM>.

As shown in <FIG>, the floating body <NUM> of the compressor <NUM> may open the main flow path <NUM> during operation of the compressor <NUM>. That is, the floating body <NUM> may open the refrigerant inlet <NUM> and the refrigerant outlet <NUM>. In other words, during operation of the compressor <NUM>, the refrigerant may flow into the valve through the refrigerant inlet <NUM> connected to the internal space <NUM> of the compressor <NUM>. The refrigerant flowing in through the refrigerant inlet <NUM> may flow to the second discharge tube 12b through the valve chamber <NUM> and the refrigerant outlet <NUM>. In this case, the bypass inlet <NUM> and the bypass outlet <NUM> may be blocked by the floating body <NUM>.

As shown in <FIG>, the floating body <NUM> may block the main flow path <NUM> when the compressor <NUM> is stopped. The floating body <NUM> may block the refrigerant inlet <NUM> and the refrigerant outlet <NUM>. In this case, the floating body <NUM> may open the bypass flow path <NUM>. For example, the floating body <NUM> may open the bypass inlet <NUM> and the bypass outlet <NUM>. In other words, when the compressor <NUM> is stopped, the refrigerant flowing in through the bypass inlet <NUM> connected to the internal space <NUM> may pass through the valve chamber <NUM> and flow to a space connected to a suction port <NUM> through the bypass outlet <NUM> and the connection flow path <NUM>. Accordingly, the internal space <NUM> and the compression chambers <NUM> and <NUM> may reach a balanced pressure in the same way as in <FIG>.

Claim 1:
A compressor (<NUM>), comprising:
a casing (<NUM>);
a driving unit (<NUM>) disposed in the casing (<NUM>);
a compression unit (<NUM>), coupled to the driving unit (<NUM>), configured to compress a refrigerant; and
a valve (<NUM>) configured to control a flow of the refrigerant in the casing (<NUM>), wherein the valve (<NUM>) includes:
a valve chamber (<NUM>) including a main flow path (<NUM>), in which the refrigerant is to flow, the main flow path (<NUM>) including a refrigerant inlet (<NUM>) and a refrigerant outlet (<NUM>),
characterized in that
a floating body (<NUM>) disposed in the valve chamber (<NUM>) to open or close the main flow path (<NUM>), and
a bypass flow path (<NUM>), formed in the valve chamber (<NUM>), to be opened or closed by the floating body (<NUM>), and when the driving unit (<NUM>) is stopped and the bypass flow path (<NUM>) is opened by the floating body (<NUM>), to allow the refrigerant to be detoured to the bypass flow path (<NUM>).