Patent Description:
A compressor refers to a mechanical device that increases pressure by compressing gas, and is divided into a reciprocating type compressor and a rotary type compressor according to the operating principle. The reciprocating type compressor is a type that converts a rotational motion of a motor into a linear reciprocating motion of a piston in a cylinder through a crankshaft and a connecting rod to suck and compress gas. Examples of the rotary type compressor include a rotary compressor that sucks and compresses gas while a roller rotates in a cylinder by a rotational motion of a motor and a scroll compressor that continuously sucks and compresses gas while a turning scroll performs an orbital motion in a certain direction from a center of a fixed scroll by a rotational motion of a motor. The existing compressor has one discharge hole and a discharge valve optimized for an operating speed (rpm) of a displacement amount in a cylinder.

A constant-speed type compressor needs to increase a size of a discharge hole in order to secure a flow rate of a discharge refrigerant and reduce a flow resistance. The enlargement of the size of the discharge hole increases a dead volume and a size of a discharge valve. The increase in the dead volume causes a decrease in cooling power, and the increase in the size of the discharge valve increases the noise due to the increase in the amount of impact, thereby reducing reliability.

In a variable type compressor, compression efficiency decreases when an operating speed of a wide range exceeds a specific range where peak efficiency occurs. In consideration of the compression efficiency aspect of the variable compressor, it is advantageous to reduce the size of the discharge hole in low-speed operation, but it is advantageous to enlarge the discharge hole in high-speed operation. As a result, the overcompression generation width increases according to the behavior of the discharge valve, so the compression efficiency decreases.

In order to solve the problems of the single discharge port and the discharge valve, a compressor employing a plurality of discharge holes and discharge valves has been disclosed. However, such a plurality of discharge holes and discharge valves are an obstacle to the compaction of the compressor due to the increase in the occupied area. In addition, individually installing the plurality of discharge valves corresponding to the plurality of discharge holes causes not only an increase in manufacturing cost but also inconvenience of maintenance.

<CIT> discloses a compressor configured to decrease a suction flow resistance and discharge flow resistance of gas sucked into and discharged out of the compressor.

<CIT> discloses a compressor configured to vary the number of discharge openings in an open state depending on the pressure and rate of flow of discharge gas during operation.

<CIT> discloses a backer for a reed valve configured to protect the reed valve against overflexing.

<CIT> discloses a compressor valve arrangement with the discharge holes arranged on an arc of circle and straight extending valve necks.

Accordingly, an object of the disclosure is to provide a compact compressor and an electronic device using the same.

Accordingly, an object of the disclosure is to provide a compressor capable of improving production cost, part management, and assembling performance, and an electronic device using the same.

According to the invention, there is provided a compressor according to claim <NUM>.

According to the disclosure, it is possible to provide the compact compressor by reducing the occupied area of the plurality of discharge valves while effectively controlling the discharge amount of the compressed gas through the plurality of discharge ports and discharge valves.

Further, in the compressor according to the discourse, since the plurality of discharge valves may be manufactured to be compact and integral, it is possible to reduce the production cost and improve the part management and assembly performance.

Hereinafter, in this document, a compressor <NUM> used in electronic devices such as an air conditioner, a refrigerator, and a freezer will be described in detail with reference to the accompanying drawings. Embodiments described below describe a sealed reciprocating type compressor <NUM> to aid understanding of the disclosure, which is illustrative. Unlike the embodiments described herein, it should be understood that various modifications such as a rotary type compressor and a scroll compressor may be implemented. However, when it is decided that a detailed description for the known functions or components related to the disclosure may obscure the gist of the disclosure, the detailed description and concrete illustration will be omitted.

<FIG> is a perspective view illustrating a sealed reciprocating type compressor <NUM>. The sealed reciprocating type compressor <NUM> is accommodated in an inner space of a container <NUM> in a sealed state. The container <NUM> is configured by combining an upper container <NUM>-<NUM> and a lower container <NUM>-<NUM> while accommodating the compressor <NUM>.

<FIG> is a perspective view illustrating the compressor <NUM> of <FIG>, and <FIG> is a cross-sectional view taken along line A-A of <FIG>.

Referring to <FIG> and <FIG>, the compressor <NUM> includes a motor <NUM> and a cylinder block <NUM>.

The motor <NUM> includes a rotor <NUM>, a stator <NUM> and a rotating shaft <NUM> coupled to the rotor <NUM>. The rotating shaft <NUM> includes a motor central shaft part <NUM>-<NUM> and an eccentric shaft part <NUM>-<NUM>. One end portion of a connecting rod <NUM> is coupled to the eccentric shaft part <NUM>-<NUM>. The other end portion of the connecting rod <NUM> is coupled to a piston <NUM> inserted into a compression space PS of the cylinder <NUM>. The connecting rod <NUM> converts a rotational motion of the rotor <NUM> into a linear reciprocating motion of the piston <NUM> disposed in the compression space PS.

The cylinder block <NUM> includes a cylinder <NUM> that has a cylindrical compression space PS provided therein, a piston <NUM> that is inserted into the compression space PS, a valve plate <NUM> that is provided on one side of the cylinder <NUM>, a gas suction part <NUM> that sucks gas, for example, a refrigerant from an outside, and a gas discharge part <NUM> that discharges gas compressed in the cylinder <NUM>.

<FIG> and <FIG> are schematic diagrams for explaining a gas compression process in the cylinder block <NUM> of the reciprocating type compressor <NUM>. The cylinder block <NUM> is inserted into the cylindrical compression space PS so that the piston <NUM> can reciprocate. A valve plate <NUM> is coupled to one side of the cylinder <NUM>. The valve plate <NUM> includes a suction port <NUM> that sucks gas and a discharge port <NUM> that discharges gas. The valve plate <NUM> includes a suction valve <NUM> that blocks the suction port <NUM> on an inner surface of the compression space PS and a discharge valve <NUM> that blocks the discharge port <NUM> on an outer surface of the compression space PS. The suction valve <NUM> and the discharge valve <NUM> are made of a plate material having elasticity. One side of the suction valve <NUM> and the discharge valve <NUM> is fixed and the other side thereof is a free end portion.

In <FIG>, when the piston <NUM> retreats within the cylinder <NUM>, the suction valve <NUM>, which is blocking the suction port <NUM> located on the inner surface of the valve plate <NUM>, is elastically deformed and opened by suction force. As a result, gas is sucked through the suction port <NUM> and fills the compression space PS. At this time, the discharge valve <NUM> that blocks the discharge port <NUM> located on the outer surface of the valve plate <NUM> seals the discharge port <NUM> by the suction force.

In <FIG>, when the piston <NUM> advances in the cylinder <NUM>, the gas in the compression space PS is compressed. Due to this compression force, the discharge valve <NUM> that is blocking the discharge port <NUM> located on the outer surface of the valve plate <NUM> is deformed and opened. As a result, the gas is discharged to the gas discharge part <NUM> through the discharge port <NUM>. At this time, the suction valve <NUM> that blocks the suction port <NUM> seals the suction port <NUM> by compression force.

<FIG> is an exploded perspective view illustrating the cylinder block <NUM> of the compressor <NUM>.

As illustrated in <FIG>, the cylinder block <NUM> includes a cylinder <NUM> that has the cylindrical compression space PS in a center thereof, the piston <NUM> that is inserted into the compression space PS of the cylinder <NUM>, the valve plate <NUM> that is coupled to one surface of the cylinder <NUM>, the gas suction part <NUM> that sucks gas, and the gas discharge part <NUM> that discharges gas. In addition, the cylinder block <NUM> includes a suction valve unit <NUM> that is disposed on the inner surface of the cylinder <NUM> side of the valve plate <NUM>, a discharge valve unit <NUM> that is at a position corresponding to three discharge ports <NUM>, <NUM>, and <NUM> on the outer surface of the valve plate <NUM>, a valve stopper <NUM> that covers the discharge valve unit <NUM>, and a valve keeper <NUM> that covers the valve stopper <NUM>.

The cylinder <NUM> has a substantially hexahedral shape and has the cylindrical compression space PS penetrating through the center thereof.

The piston <NUM> is inserted into the cylindrical compression space PS of the cylinder <NUM> to reciprocate back and forth. The piston <NUM> is connected to a connecting rod (<NUM> in <FIG>) at the rear of the cylinder <NUM>.

The valve plate <NUM> is coupled to the front of the cylinder <NUM>. The valve plate <NUM> is provided with one suction port <NUM> and the first to third discharge ports <NUM>, <NUM> and <NUM> that communicate with the compression space PS. The valve plate <NUM> includes a first bolt hole <NUM> that fastens a first bolt <NUM> and a second bolt hole <NUM> that fastens a second bolt <NUM>. The first bolt <NUM> fastens one end portion of the discharge valve unit <NUM>, the valve stopper <NUM>, and the valve keeper <NUM>, respectively. The second bolt <NUM> is fastened to the second bolt hole <NUM> to fix the other end portion of the valve keeper <NUM>.

The gas suction part <NUM> is a suction muffler <NUM> that reduces noise caused by the suction of gas, and a gas suction pipe <NUM> that transfers the gas passing through the suction muffler <NUM> to the suction port <NUM> of the valve plate <NUM>. The suction muffler <NUM> includes a plurality of expansion parts (not illustrated) provided therein and a connection passage (not illustrated) connecting between the plurality of expansion portions with a narrow width.

The gas discharge part <NUM> is coupled to the valve plate <NUM> with a predetermined space therein. The gas discharge part <NUM> includes an exhaust muffler (not illustrated) having a structure similar to the above-described suction muffler <NUM> in a predetermined space.

The suction valve unit <NUM> is made of a plate material having elasticity of magnitude corresponding to one surface of the cylinder <NUM> and is provided with a suction valve <NUM> and three discharge gas passage holes <NUM>, <NUM>, and <NUM>. The suction valve unit <NUM> has a valve head <NUM> that blocks the suction port <NUM> of the valve plate <NUM> to be described later, and a valve neck <NUM> that integrally extends from the valve head <NUM>. The valve neck <NUM> has the valve head <NUM> whose opposite end portion is integrally connected to the plate-shaped suction valve unit <NUM>. That is, the suction valve <NUM> may be formed in the plate-shaped suction valve unit <NUM> in a suction valve shape by a punching or shearing process. Obviously, the suction valve <NUM> may be separately manufactured instead of the punching or shearing process, and fixedly installed on the valve plate <NUM>.

The discharge valve unit <NUM> includes a fixed end portion <NUM> on one side thereof and first to third discharge valves <NUM>, <NUM>, and <NUM> integrally extending from the fixed end portion <NUM>. The first to third discharge valves <NUM>, <NUM>, and <NUM> open and close the first to third discharge ports <NUM>, <NUM>, and <NUM> of the valve plate <NUM>, respectively. One side of each of the first to third discharge valves <NUM>, <NUM>, and <NUM> is fixed and the other side thereof is free. Accordingly, the first to third discharge valves <NUM>, <NUM>, and <NUM> block the first to third discharge ports <NUM>, <NUM>, and <NUM>, respectively, and then when the gas compression force of the compression space PS reaches a predetermined range, each free end is elastically deformed and opens sequentially. The fixed end of the discharge valve unit <NUM> is provided with a pair of first bolt passage holes <NUM> through which a pair of first bolts <NUM> passes. The first bolt through hole <NUM> corresponds to the first bolt hole <NUM> of the valve plate <NUM>.

The valve stopper <NUM> is disposed to cover the first to third discharge ports <NUM>, <NUM>, and <NUM>. The valve stopper <NUM> includes a stopper body <NUM>, a fixed end portion <NUM> located at one end of the stopper body <NUM>, and a free end portion <NUM> located at the other end thereof. The stopper body <NUM> is bent upward at a predetermined angle from the fixed end portion <NUM> toward the free end portion <NUM>. As a result, even if the first to third discharge valves <NUM>, <NUM>, and <NUM> are deformed, the deformation of the first to third discharge valves <NUM>, <NUM>, and <NUM> is limited by the stopper body <NUM> of the valve stopper <NUM>. The fixed end portion <NUM> of the valve stopper <NUM> is provided with a pair of second bolt holes <NUM> which a pair of first bolts <NUM> passes through. The second bolt through hole <NUM> corresponds to the first bolt through hole <NUM> of the discharge valve unit <NUM> and the first bolt hole <NUM> of the valve plate <NUM>.

The valve keeper <NUM> is disposed to cover the valve stopper <NUM>. The valve keeper <NUM> includes a keeper body <NUM>, a first fixed end portion <NUM> located at one end of the keeper body <NUM>, and a second fixed end portion <NUM> located at the other end thereof. The keeper body <NUM> is bent to be upwardly inclined from a first fixed end portion <NUM> and then downwardly bent at the end. The valve keeper <NUM> restricts the valve stopper <NUM> from being deformed to a predetermined angle or more to prevent the first to third discharge valves <NUM>, <NUM>, and <NUM> and the valve stopper <NUM> from being excessively deformed. A pair of first bolts <NUM> is fastened to the first fixed end portion <NUM>. A second fixing bolt is fixed to the second fixed end portion <NUM>. The first fixing bolt <NUM> sequentially passes through the second bolt through hole <NUM> of the valve stopper <NUM> and the first bolt through hole <NUM> of the discharge valve unit <NUM>, and then is fastened to the first bolt hole <NUM>. The second fixing bolt <NUM> is fastened to the second bolt hole <NUM> of the valve plate <NUM>.

<FIG> is a plan view illustrating the discharge valve unit <NUM> according to an implementation that is not within the scope of the claims. As illustrated, the discharge valve unit <NUM> includes the first to third discharge valves <NUM>, <NUM>, and <NUM> disposed on the same plane. The first to third discharge valves <NUM>, <NUM>, and <NUM> are integrally connected to the fixed end portion <NUM> of a unitary body. The first to third discharge valves <NUM>, <NUM>, and <NUM> may be provided with individual fixed end portions. The discharge valve unit <NUM> is not limited only to three discharge valves, and may include two or four or more discharge valves.

The first discharge valve <NUM> includes a circular first valve head <NUM> that covers the first discharge port <NUM> of the valve plate <NUM> and a first valve neck <NUM> that branches into two from the first valve head <NUM> with a first space <NUM> therebetween and extends to the fixed end portion <NUM>.

The second discharge valve <NUM> is accommodated in the first space part <NUM>. The second discharge valve <NUM> includes a circular second valve head <NUM> that covers the second discharge port <NUM> of the valve plate <NUM> and a second valve neck <NUM> that branches into two from the second valve head <NUM> with a second space <NUM> therebetween and extends to the fixed end portion <NUM>.

The third discharge valve <NUM> is accommodated in the second space part <NUM>. The third discharge valve <NUM> includes a circular third valve head <NUM> that covers the third discharge port <NUM> of the valve plate <NUM> and a third valve neck <NUM> that extends in a straight line from the third valve head <NUM> to the fixed end portion <NUM>.

As described above, the first valve neck <NUM> of the first discharge valve <NUM> extends surrounding the second discharge valve <NUM>, and the second valve neck <NUM> of the second discharge valve <NUM> extends surrounding the third discharge valve <NUM>.

The first to third discharge valves <NUM>, <NUM>, and <NUM> are not limited only to the shape illustrated in <FIG>, but various modifications may be made within the scope of the disclosure. For example, the first discharge valve <NUM> may accommodate the second discharge valve <NUM> in the same plane, and the third discharge valve <NUM> may be designed to be separated from the first and second discharge valves <NUM> and <NUM>.

<FIG> is a view illustrating an open state of the first to third discharge valves <NUM>, <NUM>, and <NUM>. As illustrated, the first discharge valve <NUM>, the second discharge valve <NUM>, and the third discharge valve <NUM> are sequentially opened to a height of about <NUM>, a height of about <NUM>, and a height of about <NUM>. As such, the first to third discharge valves <NUM>, <NUM>, and <NUM> may be sequentially opened due to a difference in rigidity due to different lengths of the first to third valve necks <NUM>, <NUM>, and <NUM>. That is, the first valve neck <NUM> having the longest length, the second valve neck <NUM> having the intermediate length, and the third valve neck <NUM> having the shortest length may be sequentially opened. Obviously, each of the above-described discharge valves <NUM>, <NUM>, and <NUM> is an example, and an opening height may be adjusted by adjusting the rigidity by designing different lengths or widths.

Hereinafter, the operation of the discharge valve unit <NUM> will be described with reference to <FIG>. As illustrated, the first to third discharge ports <NUM>, <NUM>, and <NUM> are arranged in a vertical linear direction in the compression space PS of the cylinder <NUM>. In the discharge valve unit <NUM>, the first to third valve heads <NUM>, <NUM>, and <NUM> cover the first to third discharge ports <NUM>, <NUM>, and <NUM>, respectively. In addition, the first to third valve necks <NUM>, <NUM>, and <NUM> extend along the arrangement direction of the first to third discharge ports <NUM>, <NUM>, and <NUM>, that is, in the vertical linear direction. At this time, the first to third valve necks <NUM>, <NUM>, and <NUM> have a shape surrounding the circular valve heads <NUM>, <NUM>, and <NUM> in a circular curve.

The first to third discharge valves <NUM>, <NUM>, and <NUM> are sequentially opened in order of less rigidity when the pressure inside the cylinder rises above a certain level. When the motor is operated at a low speed, for example, <NUM>,<NUM> rpm, the first discharge valve <NUM> with low rigidity due to the relatively low internal pressure of the cylinder opens first and larger, and the second discharge valve <NUM> in the middle is opened later and smaller than the first discharge valve <NUM>, and the opening of the third discharge valve <NUM> having the relatively highest rigidity is restricted. On the other hand, when the motor is operated at a high speed, for example, <NUM>,<NUM> rpm, the opening amount of the third discharge valve <NUM> having high rigidity due to a relatively high internal pressure of the cylinder may be increased.

According to the characteristics of the disclosure, the first to third discharge valves <NUM>, <NUM> and <NUM> may perform the following roles.

The first discharge valve <NUM> serves to reduce the peak pressure and improve an input of low rpm together with the second discharge valve <NUM>.

The second discharge valve <NUM> serves to naturally connect the valve opening/closing delay of the first and third discharge valves <NUM> and <NUM>. In addition, the second discharge valve <NUM> reduces the peak pressure together with the first discharge valve <NUM> and is limited in opening at a relatively low pressure at a low rpm, thereby optimizing the efficiency of the first discharge valve.

The third discharge valve <NUM> may affect the occurrence and period of pressure peaks and prevent a decrease in cooling power due to low valve stiffness at high rpm, and the opening is limited for a relatively low pressure at a low rpm, so the first and second discharge valves <NUM> and <NUM> may optimize compression efficiency.

Table <NUM> below shows the peak discharge pressure generated by the operation area of the compressor, and <FIG> each are graphs illustrating the peak discharge pressure according to the change in the volume (cm<NUM>) of the compression space PS of the cylinder <NUM> at the low speed, the medium speed, and the high speed operation.

In <FIG>, when the compression space PS of the cylinder <NUM> is compressed at <NUM>,<NUM> rpm, the first discharge valve <NUM> of the disclosure starts to open, the second discharge valve <NUM> is sequentially opened, and the third discharge valve <NUM> is restricted from opening. A maximum peak discharge pressure is improved by about <NUM>% compared to the prior art. In <FIG>, when the compression space PS of the cylinder <NUM> is compressed at <NUM>,<NUM> rpm, the first discharge valve <NUM> of the disclosure starts to open, the second discharge valve <NUM> and the third discharge valve <NUM> are sequentially opened. At this time, the maximum peak discharge pressure is improved by about <NUM>% compared to the prior art. In <FIG>, when the compression space PS of the cylinder <NUM> is compressed at <NUM>,<NUM> rpm, the first discharge valve <NUM> of the disclosure starts to open, the second discharge valve <NUM> and the third discharge valve <NUM> are sequentially opened. At this time, the maximum peak discharge pressure is improved by about <NUM>% compared to the prior art.

As described above, since the compressor <NUM> to which the plurality of discharge ports <NUM>, <NUM>, and <NUM> are applied may be designed to have a relatively smaller inner diameter of each discharge port <NUM>, <NUM>, and <NUM> than the conventional compressor using one discharge port, it is possible to equally or additionally secure the flow rate of the discharged gas and minimize the flow resistance.

In addition, when the size of the plurality of discharge ports <NUM>, <NUM>, and <NUM> is reduced, the size of the corresponding plurality of discharge valves <NUM>, <NUM>, and <NUM> may also be reduced, so the impact when the discharge valves <NUM>, <NUM>, and <NUM> are opened or closed may be reduced, thereby improving the reliability and the noise problem.

In addition, the plurality of discharge valves <NUM>, <NUM>, and <NUM> are each sequentially opened and closed due to different stiffness, and as a result, it is possible to improve the compression efficiency by improving the overcompression of gas. Such sequential opening and closing may be controlled by differently designing the sizes of the inner diameters of each of the plurality of discharge ports <NUM>, <NUM>, and <NUM>, the widths of each of the valve necks, and the lengths of the valve necks.

In addition, the first to third valve necks <NUM>, <NUM>, and <NUM> extend along the arrangement direction of the plurality of discharge ports <NUM>, <NUM>, and <NUM>, thereby narrowing the spacing of the plurality of discharge ports <NUM>, <NUM>, and <NUM>.

The plurality of discharge valves <NUM>, <NUM>, and <NUM> have the same number of valves as the plurality of discharge ports <NUM>, <NUM>, and <NUM>, but may be integrally formed. In this way, when the plurality of discharge valves <NUM>, <NUM>, and <NUM> are integrally manufactured, it is possible to improve the production cost, the part management, and the assembly performance.

In addition, since the plurality of discharge valves <NUM>, <NUM>, and <NUM> operate in the same direction as the straight line connecting the center lines of the plurality of discharge valves <NUM>, <NUM>, and <NUM> and are manufactured integrally, the plurality of discharge valves <NUM>, <NUM>, and <NUM> may occupy the minimum space, and thus the compact design may be implemented, thereby further increasing the rigidity difference between the discharge valves within a limited space.

<FIG> is a plan view illustrating a discharge valve unit <NUM> of another implementation that is not within the scope of the claims. As illustrated, the discharge valve unit <NUM> includes the first to third discharge valves <NUM>, <NUM>, and <NUM> disposed on the same plane. The first to third discharge valves <NUM>, <NUM>, and <NUM> are integrally connected to the fixed end portion <NUM> of a unitary body.

The first to third discharge ports <NUM>, <NUM>, and <NUM> are arranged in the vertical linear direction in the compression space PS of the cylinder <NUM>. In the discharge valve unit <NUM>, the first to third valve heads <NUM>, <NUM>, and <NUM> cover the first to third discharge ports <NUM>, <NUM>, and <NUM>, respectively. In addition, the first to third valve necks <NUM>, <NUM>, and <NUM> extend along the arrangement direction of the first to third discharge ports <NUM>, <NUM>, and <NUM>, that is, in the vertical linear direction.

The first discharge valve <NUM> includes a quadrangular first valve head <NUM> that covers the first discharge port <NUM> of the valve plate <NUM> and a linear first valve neck <NUM> that branches into two from the first valve head <NUM> with a first space therebetween and extends to the fixed end portion <NUM>. The first discharge valve <NUM> accommodates the second discharge valve <NUM> and the third discharge valve <NUM> on the same plane in a predetermined first space.

The second discharge valve <NUM> is accommodated in the first space in the first discharge valve <NUM>. The second discharge valve <NUM> includes a quadrangular second valve head <NUM> that covers the second discharge port <NUM> of the valve plate <NUM> and a second valve neck <NUM> that branches into two from the second valve head <NUM> with a second space therebetween and extends to the fixed end portion <NUM>. The second discharge valve <NUM> accommodates the third discharge valve <NUM> on the same plane.

The third discharge valve <NUM> is accommodated in the second space. The third discharge valve <NUM> includes a quadrangular third valve head <NUM> that covers the third discharge port <NUM> of the valve plate <NUM> and a third valve neck <NUM> that extends in a straight line from the third valve head <NUM> to the fixed end portion <NUM>.

As described above, in the discharge valve unit <NUM> according to of this implementation, the first to third valve necks <NUM>, <NUM>, and <NUM> may extend along the arrangement direction of the plurality of discharge ports <NUM>, <NUM>, and <NUM>, thereby narrowing the spacing of the plurality of discharge ports <NUM>, <NUM>, and <NUM>.

<FIG> is a plan view illustrating the discharge valve unit <NUM> of another implementation that is not within the scope of the claims. As illustrated, the discharge valve unit <NUM> includes the first to third discharge valves <NUM>, <NUM>, and <NUM> disposed on the same plane. The first to third discharge valves <NUM>, <NUM>, and <NUM> are integrally connected to the fixed end portion <NUM> of a unitary body.

The first to third discharge ports <NUM>, <NUM>, and <NUM> are arranged in the circumferential direction in the compression space PS of the cylinder <NUM>. In the discharge valve unit <NUM>, the first to third valve heads <NUM>, <NUM>, and <NUM> cover the first to third discharge ports <NUM>, <NUM>, and <NUM>, respectively. In addition, the first to third valve necks <NUM>, <NUM>, and <NUM> extend along the arrangement direction of the first to third discharge ports <NUM>, <NUM>, and <NUM>, that is, in the circumferential direction.

The first discharge valve <NUM> includes a first valve head <NUM> that covers the first discharge port <NUM> of the valve plate <NUM> and a curved first valve neck <NUM> that branches into two from the first valve head <NUM> with a first space therebetween and extends to the fixed end portion <NUM>. The first discharge valve <NUM> accommodates the second discharge valve <NUM> and the third discharge valve <NUM> on the same plane in a predetermined first space.

The second discharge valve <NUM> is accommodated in the first space in the first discharge valve <NUM>. The second discharge valve <NUM> includes a second valve head <NUM> that covers the second discharge port <NUM> of the valve plate <NUM> and a curved second valve neck <NUM> that branches into two from the second valve head <NUM> with a second space therebetween and extends to the fixed end portion <NUM>. The second discharge valve <NUM> accommodates the third discharge valve <NUM> on the same plane.

The third discharge valve <NUM> is accommodated in the second space. The third discharge valve <NUM> includes a third valve head <NUM> that covers the third discharge port <NUM> of the valve plate <NUM> and a curved third valve neck <NUM> that extends from the third valve head <NUM> toward the fixed end portion <NUM>.

As described above, in the discharge valve unit <NUM> according to this implementation, the first to third valve necks <NUM>, <NUM>, and <NUM> may extend along the arrangement direction of the plurality of discharge ports <NUM>, <NUM>, and <NUM>, thereby narrowing the spacing of the plurality of discharge ports <NUM>, <NUM>, and <NUM>.

<FIG> is a plan view illustrating a discharge valve unit <NUM> according to an embodiment of the invention. As illustrated, the discharge valve unit <NUM> includes the first to third discharge valves <NUM>, <NUM>, and <NUM> disposed on the same plane. The first to third discharge valves <NUM>, <NUM>, and <NUM> are integrally connected to the fixed end portion <NUM> of a unitary body.

The first to third discharge ports <NUM>, <NUM>, and <NUM> are arranged in the vertical linear direction in the compression space PS of the cylinder <NUM>. In the discharge valve unit <NUM>, the first to third valve heads <NUM>, <NUM>, and <NUM> cover the first to third discharge ports <NUM>, <NUM>, and <NUM>, respectively. In addition, the first to third valve necks <NUM>, <NUM>, and <NUM> are perpendicular to a straight line A passing through the center of the first to third discharge ports <NUM>, <NUM>, and <NUM> and extends toward a point P on a straight line B passing through the center of the second discharge port <NUM>.

The first discharge valve <NUM> includes a quadrangular first valve head <NUM> that covers the third discharge port <NUM> of the valve plate <NUM> and a first valve neck <NUM> that extends so that a width thereof gradually decreases from the first valve head <NUM> toward the point P.

The second discharge valve <NUM> includes a quadrangular second valve head <NUM> that covers the second discharge port <NUM> of the valve plate <NUM> and a second valve neck <NUM> extends so that a width thereof gradually decreases from the second valve head <NUM> toward the point P.

The third discharge valve <NUM> includes a quadrangular third valve head <NUM> that covers the third discharge port <NUM> of the valve plate <NUM> and a third valve neck <NUM> that extends so that a width thereof gradually decreases from the third valve head <NUM> toward the point P.

As described above, in the discharge valve unit <NUM> according to the embodiment of the invention, the first to third valve necks <NUM>, <NUM>, and <NUM> extend so that the width thereof decreases toward one point P, and as a result, the plurality of discharge ports <NUM>, <NUM>, and <NUM> can be arranged very close to each other so that an angle (α) therebetween is <NUM>° or less.

<FIG> is a plan view illustrating an inner diameter Sr of the cylinder of the disclosure and inner diameters V1r, V2r, and V3r of the first to third discharge ports <NUM>, <NUM>, and <NUM>. The sum of the inner diameters V1r, V2r, and V3r of the first to third discharge ports <NUM>, <NUM>, <NUM> is preferably <NUM>% or less of the inner diameter Sr of the cylinder. If the sum of the inner diameters exceeds <NUM>%, the interference between the adjacent discharge ports occurs and the compression efficiency decreases.

Each inner diameter V1r, V2r, and V3r of the first to third discharge ports <NUM>, <NUM>, and <NUM> may be set variously within a range of <NUM>% or less of the inner diameter Sr of the cylinder, and may all be set equally to, for example, <NUM>%, and may be all set differently.

As described above, according to an aspect of the present disclosure regarding to a compressor including a compression cylinder configured to have a plurality of discharge ports for discharging compressed gas provided in a predetermined direction and a plurality of discharge valves configured to be provided in the plurality of discharge ports to control an amount of discharged gas, in which each of the discharge valves includes a valve neck configured to have one end fixed in a plate shape having elasticity and extend along an arrangement direction of the plurality of discharge ports from the one end and a valve head configured to be provided at the other end of the valve neck to cover each of the discharge ports, it is possible to manufacture the compressor compactly and reduce manufacturing and maintenance costs of the compressor by reducing the area occupied by the plurality of discharge valves.

Also, the valve neck of at least one of the plurality of discharge valves may surround and extend at least some of the other discharge valves, thereby reducing the area occupied by the plurality of discharge valves, the plurality of discharge valves may be sequentially opened, thereby preventing the overcompression of gas, and the plurality of valve necks may be integrally fixedly supported, so the plurality of discharge valves may be configured integrally.

Also, a valve stopper of the compressor that restricts deformation of the plurality of discharge valves may extend along an arrangement direction of the plurality of discharge ports to cover all of the plurality of discharge valves, and a valve keeper of the compressor that restricts maximum deformation of the plurality of discharge valves may extend along the arrangement direction of the plurality of discharge ports to cover all of the plurality of discharge valves, thereby reducing the manufacturing and maintenance costs.

Also, at least one of the plurality of discharge valves may be provided in the other discharge valves, and the plurality of discharge ports may be arranged in a linear direction, and the plurality of discharge valves may extend in a straight line along the linear direction, thereby reducing the area occupied by the plurality of discharge valves.

Also, the plurality of discharge ports may be arranged in a circumferential direction of a predetermined curvature, and the plurality of discharge valves may extend along the circumferential direction, thereby reducing the area occupied by the plurality of discharge valves, and the plurality of discharge ports may have different diameters, thereby easily controlling the discharge amount of gas.

Claim 1:
A compressor, comprising:
a compression cylinder (<NUM>) configured to have a cylinder that forms a compression space (PS) for compressing gas and a valve plate (<NUM>) that has a plurality of discharge ports (<NUM>, <NUM>, <NUM>) for discharging the compressed gas provided along a predetermined direction in which a straight line passes through a plurality of centres of the plurality of discharge ports; and
a plurality of discharge valves comprising:
a plurality of valve heads (<NUM>, <NUM>, <NUM>) that are provided to cover the plurality of discharge ports (<NUM>, <NUM>, <NUM>), and
a plurality of valve necks (<NUM>, <NUM>, <NUM>) that extend toward a point of intersection of a plurality of centre lines, the point of intersection being on a line perpendicular to the straight line,
wherein at least one of the plurality of valve necks extends to a different length from the plurality of valve heads to the point of intersection and gradually narrows toward the point of intersection.