SCROLL COMPRESSOR

BACKGROUND
Field

This specification relates to a scroll compressor, and more particularly, a capacity varying apparatus for a scroll compressor.

Background

A scroll compressor is a compressor which is provided with a non-orbiting scroll provided in an inner space of a casing, and an orbiting scroll engaged with the non-orbiting scroll to perform an orbiting motion so as to form a pair of compression chambers, each of which includes a suction chamber, an intermediate pressure chamber and a discharge chamber, between a non-orbiting wrap of the non-orbiting scroll and an orbiting wrap of the orbiting scroll.

Compared with other types of compressors, the scroll compressor is widely used for refrigerant compression in an air-conditioning apparatus and the like, by virtue of advantages of obtaining a relatively high compression ratio and stable torques resulting from smoothly-performed suction, compression and discharge strokes of a refrigerant.

Scroll compressors may be classified into a high pressure type and a low pressure type according to a type of supplying a refrigerant into a compression chamber. The high pressure type compressor employs a method in which a refrigerant is introduced directly into a suction chamber without passing through an inner space of a casing and then discharged via the inner space of the casing. In this type compressor, most of the inner space of the casing form a high pressure portion as a discharge space. On the other hand, the low pressure type scroll compressor employs a method in which a refrigerant is introduced indirectly into the suction chamber via the inner space of the casing. In this type compressor, the inner space of the casing is divided into a low pressure portion as a suction space and a high pressure portion as a discharge space by a high/low pressure dividing plate.

FIG. 1 is a longitudinal sectional view of a low pressure type scroll compressor according to the related art.

As illustrated in FIG. 1, the low pressure type scroll compressor according to the related art includes a driving motor 20 disposed in an inner space 11 of a hermetic casing 10 to generate a rotation force, and a main frame 30 disposed at an upper side of the driving motor 20.

The orbiting wrap 40 is disposed on an upper surface of the main frame 30 to be orbited by an Oldham-ring (not illustrated), and the non-orbiting scroll 50 is provided on an upper side of the orbiting scroll 40 to be engaged with the orbiting scroll 40 and thus form compression chambers P.

A rotation shaft 25 is coupled to a rotor 22 of the driving motor 20, the orbiting scroll 40 is eccentrically coupled to the rotation shaft 25, and the non-orbiting scroll 50 is coupled to the main frame 30 in a manner of being restricted from being orbited.

A back pressure chamber assembly 60 for preventing the non-orbiting scroll 50 from being raised up due to pressure of the compression chamber P during an operation is coupled to an upper side of the non-orbiting scroll 50. The back pressure chamber assembly 60 is provided with a back pressure chamber 60a in which a refrigerant of intermediate pressure is filled.

A high/low pressure dividing plate 15 is provided on an upper side of the back pressure chamber assembly 60. The high/low pressure dividing plate 15 supports a rear surface of the back pressure chamber assembly 60 and simultaneously divides the inner space 11 of the casing 10 into a low pressure portion 11 as a suction space and a high pressure portion 12 as a discharge space.

The high/low pressure dividing plate 15 has an outer circumferential surface attached to an inner circumferential surface of the casing 10 in a welding manner, and is provided with a discharge hole 15a formed through a central portion thereof to communicate with a discharge port 54 of the non-orbiting scroll 50.

In the drawing, a non-explained reference numeral 13 denotes a suction pipe, 14 denotes a discharge pipe, 18 denotes a sub frame, 21 denotes a stator, 21a denotes a winding coil, 41 denotes a disk portion of the orbiting scroll, 42 denotes the orbiting wrap, 51 denotes a disk portion of the non-orbiting scroll, 52 denotes the non-orbiting wrap, 53 denotes a suction port, and 61 denotes a modulation ring for varying a capacity.

With the configuration of the related art scroll compressor, when a rotation force is generated in the driving motor 20 in response to power supplied to the driving motor 20, the rotation shaft 25 transfers the rotation force of the driving motor 20 to the orbiting scroll 40.

The orbiting scroll 40 then performs an orbiting motion with respect to the non-orbiting scroll 50 by the Oldham-ring. Accordingly, a pair of compression chambers P is formed between the orbiting scroll 40 and the non-orbiting scroll 50 such that a refrigerant can be sucked, compressed and discharged.

In this instance, the refrigerant compressed in the compression chambers P is partially introduced from the intermediate pressure chamber into the back pressure chamber 60a through a back pressure hole (not illustrated). The refrigerant of intermediate pressure introduced into the back pressure chamber 60a generates back pressure to lift a floating plate 65 constructing the back pressure chamber assembly 60. The floating plate 65 is closely adhered on a lower surface of the high/low pressure dividing plate 15 such that the high pressure portion 12 and the low pressure portion 11 are divided from each other. Simultaneously, pressure of the back pressure chamber pushes the non-orbiting scroll 50 toward the orbiting scroll 40, to maintain the compression chamber P between the non-orbiting scroll 50 and the orbiting scroll 40 in an air-tight state.

Here, the scroll compressor, similar to other types of compressors, may vary a compression capacity according to requirement of a refrigerating device with the compressor. For example, as illustrated in FIG. 1, the modulation ring 61 and a lift ring 62 are additionally provided on the disk portion 51 of the non-orbiting scroll 50, and a control valve 63 which communicates with the back pressure chamber 60a through a first communication passage 61a is provided on one side of the modulation ring 61. A second communication passage 61b is formed between the modulation ring 61 and the lift ring 62, and a third communication passage 61c which is open when the modulation ring 61 rises is formed between the modulation ring 61 and the non-orbiting scroll 50. One end of the third communication passage 61c communicates with the intermediate compression chamber P and another end thereof communicates with the low pressure portion 11 of the casing 10.

During a power operation (mode) of the scroll compressor, as illustrated in FIG. 2A, the control valve 63 closes the first communication passage 61a and opens the second communication passage 61b to communicate with the low pressure portion 11, thereby preventing the modulation ring 61 from being raised up. Accordingly, the third communication passage 61c is maintained in a closed state.

On the other hand, during a power-saving operation (mode) of the scroll compressor, as illustrated in FIG. 2B, the control valve 63 communicates the first communication passage 61a with the second communication passage 61b. Accordingly, the modulation ring 61 is raised up to open the third communication passage 61c, such that the refrigerant within the intermediate compression chamber P is partially leaked into the low pressure portion 11. This results in a reduction of a capacity of the compressor.

However, the capacity varying apparatus of the related art scroll compressor which includes the modulation ring 61, the lift ring 62 and the control valve 63 requires such a lot of components. Also, the first communication passage 61a, the second communication passage 61b and the third communication passage 61c should be formed on the modulation ring 61 to operate the modulation ring 61, which makes the structure of the modulation ring 61 complicated.

Furthermore, the capacity varying apparatus of the related art scroll compressor should fast lift the modulation ring 61 using the refrigerant of the back pressure chamber 60a. However, as the modulation ring 61 is formed in a ring shape and coupled with the control valve 63, a weight of the modulation ring 61 increases which makes it difficult to fast lift the modulation ring 61. In addition, a passage for lifting the modulation ring 61 is long and even the refrigerant should be introduced into a space between the modulation ring 61 and the lift ring 62 to lift the modulation ring 61, but the pressure of the back pressure chamber 60a still exists on the upper surface of the modulation ring 61. Therefore, the lifting of the modulation ring 61 is not easy and responsiveness of the valve is lowered, which results in interfering with a fast control of the variation of the capacity of the compressor.

In the capacity varying apparatus of the related art scroll compressor, a bypass hole and a control valve 63 for opening and closing the bypass hole are structurally unable to be employed. Accordingly, upon an occurrence of over-compression in a corresponding operation mode, the apparatus is unable to appropriately handle it, which results in lowering efficiency of the compressor.

BRIEF DESCRIPTION OF THE DRAWINGS

Embodiments will be described in detail with reference to the following drawings in which like reference numerals refer to like elements, and wherein:

FIG. 1 is a longitudinal sectional view of a scroll compressor having a capacity varying apparatus according to the related art;

FIGS. 2A and 2B are longitudinal sectional views illustrating a power-operation state and a saving-operation state using the capacity varying apparatus in the scroll compressor of FIG. 1;

FIG. 3 is a longitudinal sectional view illustrating a scroll compressor having a capacity varying apparatus in accordance with the present invention;

FIG. 4 is a perspective view illustrating an inside of the scroll compressor having the capacity varying apparatus according to FIG. 3;

FIG. 5 is an exploded perspective view of one embodiment of a capacity varying apparatus according to FIG. 3;

FIG. 6 is a perspective view illustrating an assembled state and a partially-cut state of the one embodiment of the capacity varying apparatus according to FIG. 5;

FIGS. 7A and 7B are enlarged longitudinal sectional views of embodiments related to a first valve assembly in the capacity varying apparatus of FIG. 3;

FIGS. 8A and 8B are schematic views illustrating operations of a first valve assembly and a second valve assembly according to an operating mode of the compressor of FIG. 3, wherein FIG. 8A illustrates a power mode and FIG. 8B illustrates a saving mode;

FIG. 9 is an exploded perspective view of another embodiment of a capacity varying apparatus according to FIG. 3;

FIG. 10 is a rear perspective view of a back pressure plate of FIG. 9;

FIG. 11 is an enlarged longitudinal sectional view illustrating a connection structure of a first valve assembly and a second valve assembly in FIG. 9;

FIGS. 12A and 12B are schematic views illustrating operations of a first valve assembly and a second valve assembly according to an operating mode of the compressor in FIG. 9, wherein FIG. 12A illustrates a power mode, and FIG. 12B illustrates a saving mode;

FIG. 13 is a longitudinal sectional view illustrating an example that the capacity varying apparatus is provided on a non-orbiting scroll in the scroll compressor according to FIG. 3; and

FIG. 14 is a longitudinal sectional view illustrating an example that an overheat preventing unit is provided in the scroll compressor according to FIG. 3.

DETAILED DESCRIPTION

Description will now be given in detail of a scroll compressor according to exemplary embodiments disclosed herein, with reference to the accompanying drawings.

FIG. 3 is a longitudinal sectional view illustrating a scroll compressor having a capacity varying apparatus in accordance with the present invention, FIG. 4 is a perspective view illustrating an inside of the scroll compressor having the capacity varying apparatus according to FIG. 3, FIG. 5 is an exploded perspective view of one embodiment of a capacity varying apparatus according to FIG. 3, and FIG. 6 is a perspective view illustrating an assembled state and a partially-cut state of the one embodiment of the capacity varying apparatus according to FIG. 5.

As illustrated in FIG. 3, a scroll compressor according to this embodiment is configured such that a hermetic inner space of a casing 110 is divided into a low pressure portion 111 as a suction space and a high pressure portion 112 as a discharge space by a high/low pressure dividing plate 115, which is provided on an upper side of a non-orbiting scroll 150 to be explained later. Here, the low pressure portion 111 corresponds to a lower space of the high/low pressure dividing plate 115, and the high pressure portion 112 corresponds to an upper space of the high/low pressure dividing plate 115.

A suction pipe 113 communicating with the low pressure portion 111 and a discharge pipe 114 communicating with the high pressure portion 112 are fixed to the casing 110, respectively, such that a refrigerant can be sucked into the inner space of the casing 110 or discharged out of the casing 110.

The low pressure portion 111 of the casing 110 is provided with a driving motor 120 having a stator 121 and a rotor 122. The stator 121 is fixed to an inner wall surface of the casing 100 in a shrink-fitting manner, and a rotation shaft 125 is inserted into a central portion of the rotor 122. A coil 121a is wound on the stator 121. The coil 121a, as illustrated in FIGS. 3 and 4, is electrically connected to an external power supply source through a terminal 119, which is coupled through the casing 110.

A lower side of the rotation shaft 125 is rotatably supported by an auxiliary bearing 117 provided on a lower portion of the casing 110. The auxiliary bearing 117 is supported by a lower frame 118 fixed to an inner surface of the casing 110 and thus can stably support the rotation shaft 125. The lower frame 118 may be welded on an inner wall surface of the casing 110. A bottom surface of the casing 110 is used as an oil storage space. Oil stored in the oil storage space is carried upwardly by the rotation shaft 125 and the like and thus introduced into a driving unit and the compression chamber for facilitating lubrication.

An upper end portion of the rotation shaft 125 is rotatably supported by a main frame 130. The main frame 130, similar to the lower frame 118, is fixed to the inner wall surface of the casing 110. A main bearing portion 131 downwardly protrudes from a lower surface of the main frame 130, and the rotation shaft 125 is inserted into the main bearing portion 131. An inner wall surface of the main bearing portion 131 serves as a bearing surface, and supports the rotation shaft 125 together with the oil, such that the rotation shaft 125 can smoothly rotate.

An orbiting scroll 140 is disposed on an upper surface of the main frame 130. The orbiting scroll 140 includes a disk portion 141 having a shape similar to a disk, and an orbiting wrap 142 spirally formed on one side surface of the disk portion 141. The orbiting wrap 142 forms the compression chambers P together with a non-orbiting wrap 152 of the non-orbiting scroll 150 to be explained later.

The disk portion 141 of the orbiting scroll 140 orbits in a state of being supported by the upper surface of the main frame 130. An Oldham-ring 136 is interposed between the disk portion 141 and the main frame 130 to prevent self-rotation of the orbiting scroll 140.

A boss 143 in which the rotation shaft 125 is inserted is formed on a lower surface of the disk portion 141 of the orbiting scroll 140, and accordingly the orbiting scroll 140 is orbited by the rotational force of the rotation shaft 125.

The non-orbiting scroll 150 engaged with the orbiting scroll 140 are disposed on the orbiting scroll 140. Here, the non-orbiting scroll 150 is provided to be movable up and down with respect to the orbiting scroll 140. In detail, the non-orbiting scroll 150 is supported with being laid on an upper surface of the main frame 130 in a manner that a plurality of guide pins (not illustrated) inserted into the main frame 130 are inserted in a plurality of guide holes (not illustrated) formed on an outer circumferential portion of the non-orbiting scroll 150.

Meanwhile, the non-orbiting scroll 150 includes a disk portion 151 formed in a disk shape on an upper surface of a body thereof, and the non-orbiting wrap 152 spirally formed on a lower portion of the disk portion 151 and engaged with the orbiting wrap 142 of the orbiting scroll 140.

A suction port 153 through which a refrigerant existing in the low pressure portion 111 is sucked is formed through a side surface of the non-orbiting scroll 150, and a discharge port 154 through which a compressed refrigerant is discharged is formed through an approximately central portion of the disk portion 151.

As aforementioned, the orbiting wrap 142 and the non-orbiting wrap 152 form a plurality of compression chambers P. The compression chambers are reduced in volume while orbiting toward the discharge port 154, thereby compressing the refrigerant. Therefore, the lowest pressure is existing in a compression chamber adjacent to the suction port 153, the highest pressure is existing in a compression chamber communicating with the discharge port 154, and pressure of a compression chamber present therebetween is intermediate pressure which has a value between suction pressure of the suction port 153 and discharge pressure of the discharge port 154. The intermediate pressure is applied to a back pressure chamber 160a to be explained later and serves to press the non-orbiting scroll 150 toward the orbiting scroll 140. Accordingly, a scroll-side back pressure hole 151a which communicates with one of areas having the intermediate pressure and through which the refrigerant is discharged is formed on the disk portion 151, as illustrated in FIG. 5.

A back pressure plate 161 which forms a part of the back pressure chamber assembly 160 is fixed to a top of the disk portion 151 of the non-orbiting scroll 150. The back pressure plate 161 is formed approximately in an annular shape, and provided with a supporting plate 162 which is brought into contact with the disk portion 151 of the non-orbiting scroll 150. The supporting plate 162 has a shape of an annular plate with a hollow center. Also, as illustrated in FIG. 5, a plate-side back pressure hole 161d communicating with the scroll-side back pressure hole 151a is formed through the supporting plate 162.

First and second annular walls 163 and 164 are formed on an upper surface of the supporting plate 162 along an inner circumferential portion and an outer circumferential portion of the supporting plate 162. An outer circumferential surface of the first annular wall 163, an inner circumferential surface of the second annular wall 164 and the upper surface of the supporting plate 162 form the back pressure chamber 160a formed in the annular shape.

A floating plate 165 forming an upper surface of the back pressure chamber 160a is provided on an upper side of the back pressure chamber 160a. A sealing end portion 166 is disposed on an upper end portion of an inner space of the floating plate 165. In detail, the sealing end portion 166 upwardly protrudes from a surface of the floating plate 165, and has an inner diameter which is not so great to obscure an intermediate discharge port 167. The sealing end portion 166 comes in contact with a lower surface of the high/low pressure dividing plate 115, such that a discharged refrigerant can be discharged to the high pressure portion 112 without being leaked into the low pressure portion 111.

A non-explained reference numeral 156 denotes a bypass valve which opens and closes a discharge bypass hole for bypassing a part of a refrigerant compressed in an intermediate compression chamber to prevent over-compression, and 168 denotes a check valve which prevents a refrigerant discharged to the high pressure portion from flowing back into the compression chamber.

Hereinafter an operation of the scroll compressor according to the embodiment of the present invention will be described.

That is, when power is applied to the stator 121, the rotation shaft 125 rotates. The orbiting scroll 140 coupled to an upper end portion of the rotation shaft 125 performs an orbiting motion with respect to the non-orbiting scroll 150, in response to the rotation of the rotation shaft 125. Accordingly, a plurality of compression chambers P formed between the non-orbiting wrap 152 and the orbiting wrap 142 move toward the discharge port 154. During the movement, a refrigerant is compressed.

When the compression chamber P communicates with the scroll-side back pressure hole 151a before arriving at the discharge port 154, the refrigerant is partially introduced into the plate-side back pressure hole 161d formed through the supporting plate 162, which results in applying intermediate pressure to the back pressure chamber 160a that is formed by the back pressure plate 161 and the floating plate 165. Accordingly, the back pressure plate 161 is affected by pressure applied in a downward direction and the floating plate 165 is affected by pressure applied in an upward direction.

Here, since the back pressure plate 161 is coupled to the non-orbiting scroll 150 by a bolt, the intermediate pressure of the back pressure chamber 160a also affects the non-orbiting scroll 150. However, the non-orbiting scroll 150 is unable to be moved downward due to already being brought into contact with the disk portion 141 of the orbiting scroll 140, and thus the floating plate 165 is moved upward. The floating plate 165 prevents a leakage of the refrigerant from the discharge space as the high pressure portion 112 into the suction space as the low pressure portion 111, in response to the sealing end portion 166 thereof being brought into contact with a lower end portion of the high/low pressure dividing plate 115. In addition, the non-orbiting scroll 150 is pushed toward the orbiting scroll 140 by the pressure of the back pressure chamber 160a, thereby blocking the leakage of the refrigerant between the orbiting scroll 140 and the non-orbiting scroll 150.

When a capacity varying apparatus is applied to the scroll compressor according to this embodiment, capacity varying bypass holes (hereinafter, referred to as ‘bypass holes’) 151b that communicate with the intermediate pressure chamber are formed through the disk portion 151 of the non-orbiting scroll 150 in a direction from the intermediate pressure chamber toward a rear surface of the disk portion 151. The bypass holes 151b are formed with an interval of 180° with facing each other at positions in the range of 60 to 70% of a theoretical suction volume. However, when a wrap length of the orbiting wrap 142 is asymmetrically longer by 180° than a wrap length of the non-orbiting wrap 152, the same pressure is generated at the same crank angle in an inner pocket and an outer pocket. Therefore, the two bypass holes 151b may be formed at the same crank angle or only one bypass hole may be formed such that both of the inner and outer pockets communicate with each other.

A check valve 155 for opening and closing the bypass hole 151b is provided at an end portion of each of the bypass holes 151b. The check valve 155 may be configured as a reed valve which is opened and closed according to pressure of the intermediate pressure chamber.

As illustrated in FIG. 10, a plurality of valve accommodation grooves 161a in which the check valves 155 are accommodated, respectively, are formed on a lower surface of the back pressure plate 161 corresponding to the rear surface of the disk portion 151 of the non-orbiting scroll 150. The plurality of valve accommodation grooves 161a may communicate with each other through a communication groove 161b.

One end of a discharge hole 161c for guiding a bypassed refrigerant into the suction space as the low pressure portion 111 of the casing 110 is connected to one of the plurality of valve accommodation grooves 161a or the communication groove 161b. Another end of the discharge hole 161c penetrates through an outer circumferential surface of the back pressure plate 161. Accordingly, when the valve accommodation grooves 161a, the communication groove 161b and the discharge hole 161c form the intermediate pressure chamber P1, in which a refrigerant of intermediate pressure is stored, when the check valves 155 are open.

Meanwhile, as illustrated in FIGS. 3 to 7, a first valve assembly 170 is provided on an outer circumferential surface of the back pressure plate 161. The first valve assembly 170 communicates with an end portion of the discharge hole 161c and selectively opens and closes the discharge hole 161c according to an operating mode of the compressor.

The first valve assembly 170 is a type of check valve that opens and closes the discharge hole 161c while a piston valve 172 to be explained later moves according to a pressure difference between both sides thereof. The first valve assembly 170 includes a valve guide 171 having a valve space 175 and coupled to the back pressure plate 161, and a piston valve 172 slidably inserted into the valve guide 171 and opening and closing the discharge hole 161c while reciprocating in the valve space 175 according to the pressure difference.

The valve guide 171 includes therein the valve space 175 formed in a radial direction, and a differential pressure space 176 outwardly extending from the valve space 175 to apply operation pressure to a rear surface of the piston valve 172 that is inserted into the valve space 175.

Exhaust holes 175a are formed on both upper and lower sides of the valve space 175 in a manner of communicating with the discharge hole 161c. The exhaust holes 175a are open when the piston valve 172 is pushed backward, so as to guide a refrigerant discharged through the discharge hole 161c into the inner space of the casing 110 as the low pressure portion 111.

An injection hole 176a is formed on one side of the differential pressure space 176, and coupled with an end portion of a third connection pipe 183c such that the third connection pipe 183c communicates with the differential pressure space 176. Accordingly, a refrigerant of intermediate pressure or suction pressure guided along the third connection pipe 183c is selectively supplied into the differential pressure space 176 through the injection hole 176a.

As illustrated in FIG. 7A, a sectional area A1 of the differential pressure space 176 in a radial direction thereof is smaller than a sectional area A2 of the valve space 175 in a radial direction thereof. A stepped surface 176b is formed between the differential pressure space 176 and the valve space 175. The stepped surface 176b supports a rear end of the piston valve 172 to limit a pushed amount of the piston valve 172. Therefore, the injection hole 176a is formed adjacent to the differential pressure space 176 on the basis of the stepped surface 176b between the valve space 175 and the differential pressure space 176.

The sectional area A1 of the differential pressure space 176 is greater than a sectional area A3 of the discharge hole 161c in a radial direction thereof. Accordingly, upon closing the piston valve 172, even though pressure of the discharge hole 161c and pressure of the differential pressure space 176 are the same as each other, an area that pressure is applied from the differential pressure space 176 to a rear surface (back pressure surface) 172b of the piston valve 172 is greater than an area that pressure is applied from the discharge hole 161c to a front surface (open/close surface) 172a of the piston valve 172. Consequently, the piston valve 172 can be maintained in a closed state. However, even though the sectional area A1 of the differential pressure space 176 is the same as or smaller than the sectional area A3 of the discharge hole 161c, the pressure of the differential pressure pace 176 is higher than the pressure of the valve space 175. Therefore, upon switching into the power operation mode, the piston valve 172 may be moved toward the discharge hole 161c and closed.

The piston valve 172 is formed in a shape with a circular section, which has an outer diameter almost the same as an inner diameter of the valve space 175, so as to be slidable in the valve space 175. Since the piston valve 172 is moved according to a difference between the pressure of the back pressure space 176 and the pressure of the discharge hole 161c, each of the open/close surface 172a and the back pressure surface 172b of the piston valve 172 may be likely to collide with an outer side surface of the back pressure plate 161 or the stepped surface of the valve guide 171. Therefore, the piston valve 172 may preferably be formed of a material, which can minimize noise generated upon the collision with providing rigidity great enough to avoid damage due to the collision and is smoothly slidable, for example, a material such as engineer plastic.

The piston valve 172, as illustrated in FIG. 7A, may also be configured to be movable only by the pressure difference between the open/close surface 172a and the back pressure surface 172b, but in some cases, as illustrated in FIG. 7B, may further be provided with a pressing spring 173, such as a compression coil spring, on the back pressure surface 172b. In case of providing the pressing spring 173, the pressing spring 173 may push the piston valve 172 toward the front so as to prevent vibration of the piston valve 172 due to a low pressure difference between both sides of the piston valve 172, when pressure applied to a pressure-applied surface is low due to intermediate pressure failing to reach sufficient pressure, similar to the moment of starting the compressor.

Also, instead of the pressing spring, an O-ring recess (no reference numeral given) may be provided on a sliding surface of the valve guide 171 which comes in contact with an outer surface of the piston valve 172, and an O-ring 177 may be inserted into the O-ring recess. This may result in preventing a leakage of a refrigerant due to differential pressure between the valve space 175 and the exhaust holes 175a and preventing the vibration of the piston valve 172 due to the pressure difference.

Meanwhile, as illustrated in FIGS. 3 to 8B, the scroll compressor according to this embodiment includes a second valve assembly 180 for operating the first valve assembly 170. Accordingly, the second valve assembly 180 selectively applies intermediate pressure or suction pressure to the first valve assembly 170, such that the first valve assembly 170 can be operated according to a difference of back pressure applied by the second valve assembly 180.

As illustrated in FIGS. 3 and 4, the second valve assembly 180 is fixed to an outer side surface of the back pressure plate 161. The second valve assembly 180 is provided with a third inlet/outlet port 186c to be explained later. The third inlet/outlet port 186c of the second valve assembly 180 is connected with another end of a connection pipe 183 which is connected to the injection hole 176a of the first valve assembly 170. Accordingly, back pressure corresponding to suction pressure or intermediate pressure is generated in the differential pressure space 176 of the first valve assembly 170.

The second valve assembly 180 includes a manifold part 181 connected to the first valve assembly 170 to guide a refrigerant, and a valve part 182 connected to the manifold part 181 to switch a flowing direction of the refrigerant. The manifold part 181 and the valve part 182 may be formed integral with each other. However, considering that an internal passage of the manifold part 181 is formed in a complicated form, it is preferable to separately fabricate the manifold part 181 and the valve part 182 and assemble them with each other.

The manifold part 181 includes a body 185 formed in a block-like shape and coupled to an outer side surface of the back pressure plate 161 using bolts, with interposing a gasket 187 therebetween. To this end, bolt holes 185d are formed on both sides of the body 185.

The body 185 is provided therein with three passages. The first passage 185a is connected to the back pressure chamber 160a through an intermediate pressure hole 160b which will be explained later, a second passage 185b is connected to the low pressure portion 111 of the casing 110, and a third passage 185c is connected to the differential pressure space 176 of the first valve assembly 170 through a connection pipe 183 which will be explained later.

As illustrated in FIGS. 5, 8A and 8B, an inlet of the first passage 185a is formed on a surface of the body 185 brought into contact with the back pressure plate 161, and an outlet of the first passage 185a is formed on a lower surface of the body 185 brought into contact with the valve part 182. Therefore, the first passage 185a is bent from a side surface of the body 185 to the lower surface of the body 185.

Here, in order to connect the first passage 185a of the second valve assembly 180 to the back pressure chamber 160a, the intermediate pressure hole 160b should be formed from the back pressure chamber 160a to an outer circumferential surface of the back pressure plate 161 or an outer circumferential surface of the non-orbiting scroll 150 in a penetrating manner. FIG. 6 illustrates an example in which the intermediate pressure hole 160b is formed from a bottom surface of the back pressure chamber 160a to the outer circumferential surface of the back pressure plate 161 in a penetrating manner.

Also, the intermediate pressure hole 160b may be provided with a filter 160c to prevent foreign materials remaining in the back pressure chamber 160a from being introduced into the intermediate pressure hole 160b. The filter 160c may preferably be inserted into an extending recess (no reference numeral given) that is formed on an inlet of the intermediate pressure hole 160b, namely, an end portion of the bottom surface of the back pressure chamber 160a.

Meanwhile, an inlet of the second passage 185b is open toward the low pressure portion 111 of the casing 110, and may be formed on any of the other surfaces of the body 185 except for the surface brought into contact with the back pressure plate 161. The drawing illustrates an example in which the inlet of the second passage 185b is located on an opposite surface to the surface of the body 185 brought into contact with the back pressure plate 161. Also, an outlet of the second passage 185b, similar to the outlet of the first passage 185a, is formed on the lower surface of the body 185. Accordingly, the second passage 185b is bent from a side surface of the body 185 to the lower surface.

An inlet of the third passage 185c is formed on the surface with the outlet of the first passage 185a and the outlet of the second passage 185b. An outlet of the third passage 185c may be formed on any of the other surfaces of the body 185 except for the surface brought into contact with the back pressure plate 161. The drawing illustrates an example of being formed on a side surface of an upper end portion of the body 185.

Meanwhile, the valve part 182 is configured as a solenoid valve that is connected with an external power source and selectively operating a mover according to supply or non-supply of power from the external power source.

A valve housing 186 is provided thereon with a first inlet/outlet port 186a that communicates with the first passage 185a of the manifold part 181, a second inlet/outlet port 186b that communicates with the second passage 185b, and a third inlet/outlet port 186c that communicates with the third passage 185c.

A coil 182a to which power is applied is provided within the valve housing 186. A mover 182b that is moved in response to power applied to the coil 182a is provided within the coil 182a, and a return spring 182c is provided on one end of the mover 182b.

A switching valve 182d is coupled to the mover 182b. The switching valve 182d communicates the first inlet/outlet port 186a and the third inlet/outlet port 186c with each other or the second inlet/outlet port 186b and the third inlet/outlet port 186c with each other.

Accordingly, when power is applied to the coil 182a, the mover 182b and the switching valve 182d coupled to the mover 182b are moved in a first direction (a direction of closing the discharge hole) so as to communicate the passages 185a and 185c with each other. On the other hand, when power is off, the mover 182b is returned in a second direction (in a direction of opening the discharge hole) by the return spring 182c so as to communicate other passages 185b and 185c with each other. This results in switching a flowing direction of a refrigerant that flows toward the first valve assembly 170.

Here, the coil 182a of the second valve assembly 180, as illustrated in FIGS. 3 and 4, is electrically connected with the external power source through a second terminal 119b that is inserted through the casing 110. As the coil 182a of the second valve assembly 180 is electrically connected to a separate terminal, unlike a winding coil 121a of the driving motor 120, stability can be enhanced more than connecting power sources with different specifications to the same terminal.

An unexplained reference numeral 151f denotes a discharge bypass hole that bypasses a part of a refrigerant compressed in an intermediate pressure chamber to prevent over-compression, 168 denotes a check valve that prevents a refrigerant discharged to the high pressure portion from flowing back into the compression chamber, and 187 denotes a gasket.

Hereinafter, an operation of the scroll compressor according to the embodiment of the present invention will be described.

That is, during a power operation mode, as illustrated in FIG. 8A, power is applied to the valve part 182 of the second valve assembly 180 and the mover 182b is pulled toward the coil 182a accordingly.

The switching valve 182d coupled to the mover 182b is then moved toward the coil (to right in the drawing), such that the first inlet/outlet port 186a and the third inlet/outlet port 186c of the valve housing 186 communicate with each other.

Accordingly, a refrigerant of intermediate pressure of the back pressure chamber 160a is moved into the valve housing 186 through the first passage 185a connected to the first inlet/outlet port 186a, and then flows into the differential pressure space 176 of the first valve assembly 170 through the third passage 185c connected to the third inlet/outlet port 186c and the connection pipe 183.

By virtue of the refrigerant of the intermediate pressure, pressure of the differential pressure space 176 becomes intermediate pressure, which pushes the piston valve 172 of the first valve assembly 170 toward the discharge hole 161c, thereby closing the discharge hole 161c. In this instance, a front side of the piston valve 172, namely, the open/close surface 172a is brought into contact with the discharge hole 161c, which is also under intermediate pressure. However, since the sectional area A3 of the discharge hole 161c is smaller than the sectional area A1 of the differential pressure space 176, the piston valve 172 is moved toward the discharge hole 161c and closes the discharge hole 161c.

In this state, although the refrigerant stored in the intermediate pressure chamber of the compression chamber P is partially discharged into the valve accommodation groove 161a through the bypass hole 151b in a manner of opening the check valve 155, the refrigerant is maintained in a state of being filled in the valve accommodation groove 161a, the communication groove 161b and the discharge hole 161c. Accordingly, the refrigerant does not flow out of the compression chamber P any more, which results in continuing the power operation of the compressor.

On the other hand, during a saving operation mode, as illustrated in FIG. 8B, power supplied to the coil 182a of the second valve assembly 180 is blocked, and thereby the mover 182b is pushed opposite to the coil 182a by the return spring 182c.

The switching valve 182d coupled to the mover 182b is then moved to an opposite side of the coil 182a (to left in the drawing), such that the second inlet/outlet port 186b and the third inlet/outlet port 186c of the valve housing 186 communicate with each other.

In turn, the valve housing 186 communicates with the low pressure portion 111 of the casing 110 through the second passage 185b connected to the second inlet/outlet port 186b. Accordingly, a refrigerant of suction pressure flows into the valve housing 186 and then flows into the differential pressure space 176 of the first valve assembly 170 through the third passage 185c.

Pressure of the differential pressure space 176 thus becomes suction pressure. The piston valve 172 of the first valve assembly 170 is then pushed toward the differential pressure space 176 by the pressure of the discharge hole 161c, thereby opening the discharge hole 161c.

Accordingly, the refrigerant which is already filled in the valve accommodation groove 161a, the communication groove 161b and the discharge hole 161c is fast discharged into the valve space 175 of the first valve assembly 170 through the check valve 155. The refrigerant is then discharged into the low pressure portion 111 of the casing 110 through the exhaust holes 175a formed on the valve space 175. A part of the refrigerant filled in the intermediate pressure chamber of the compression chamber P is continuously discharged along the path, thereby continuing the saving operation of the compressor.

With the configuration, a bypass hole and a bypass valve for preventing over-compression can be provided between the non-orbiting scroll and the back pressure plate. Accordingly, a refrigerant compressed in an intermediate pressure chamber during over-compression can partially be bypassed, which may result in enhancing efficiency of the compressor.

Also, a valve which opens and closes a bypass passage of a refrigerant may be configured as a first valve assembly that is operated by a pressure difference, and the first valve assembly may be configured as a piston valve that is disposed outside a non-orbiting scroll and a back pressure plate and operated in response to a less pressure variation. This may allow for fast switching an operating mode of the compressor.

In addition, the first valve assembly may be disposed on an end portion of a discharge passage for a refrigerant. Accordingly, the refrigerant may already stay near an outlet port of the passage when a power operation is switched into a saving operation, which may thus allow for fast switching into the saving operation that much.

A valve that operates the first valve assembly may be configured as a second valve assembly which is configured in an electric form. This may reduce a number of components and simplify a passage for bypassing a refrigerant, thereby facilitating a fabrication and enhancing reliability for a switching operation of the first valve assembly.

Also, a second terminal for applying external power to the second valve assembly may be provided, independent of a first terminal for applying external power to the driving motor, which may allow for freely adjusting a specification of a power source that applies power to the second valve assembly, thereby enhancing stability.

Hereinafter, another embodiment for connecting the first valve assembly and the second valve assembly in a scroll compressor according to the present invention will be described.

That is, the foregoing embodiment has illustrated that the first and second valve assemblies are connected using the connection pipe provided outside the non-orbiting scroll or the back pressure plate, but this embodiment illustrates that the two valve assemblies are connected by forming a connection passage groove on the non-orbiting scroll or the back pressure plate.

For example, as illustrated in FIG. 9, a connection passage groove 161e which has an arcuate shape is formed on a lower surface of the back pressure plate 161. The connection passage groove 161e is located at an opposite side to the communication groove 161b connecting the valve accommodation grooves 161a, when projecting on a plane. Alternatively, the connection passage groove 161e may fully be formed on the lower surface of the back pressure plate 161.

However, since both ends should communicate with the first valve assembly 170 and the second valve assembly 180, respectively, the both ends of the connection passage groove 161e may be formed through an outer circumferential surface of the back pressure plate 161. That is, one end of the connection passage groove 161e may be formed through a portion of the outer circumferential surface of the back pressure plate 161 to which the second valve assembly 180 is coupled, and another end of the connection passage groove 161e is formed through another portion of the outer circumferential surface of the back pressure plate 161 to which the first valve assembly 170 is coupled.

Accordingly, since the outlet of the third passage 185c should communicate with the one end of the connection passage groove 161e, the outlet of the third passage 185c is formed on a surface of the body 185 of the second valve assembly 180, which is brought into contact with the back pressure plate 161. Also, since the injection hole 176a should communicate with the another end of the connection passage groove 161e, an inlet of the injection hole 176a is formed on a surface of the body 185, on which a valve hole 175 of the first valve assembly 170 is formed.

A connection passage groove 261c preferably overlaps a gasket 258, which is provided on an upper surface of a non-orbiting scroll 250, so as to be sealed.

In addition, the basic configuration and thusly-obtained operation effects according to this embodiment are the same/like to those of the aforementioned embodiment, so detailed description thereof will be omitted.

However, according to this embodiment, the connection passage groove 161e can be formed on the lower surface of the non-orbiting scroll 150 or the lower surface of the back pressure plate 161 contacting the non-orbiting scroll 150. Therefore, this embodiment does not have to connect a separate connection pipe to the first valve assembly and the second valve assembly, thereby reducing a number of components, followed by a reduction of a number of assembling processes. This may result in a reduction of fabricating costs. In addition, reliability can be more enhanced than employing a separate connection pipe.

Meanwhile, the valve accommodation grooves, the communication groove and the discharge hole may be formed on a rear surface of the disk portion 151 of the non-orbiting scroll 150. That is, as illustrated in FIG. 13, a plurality of valve accommodation grooves 151c are recessed by predetermined depths into the rear surface of the disk portion 151 of the non-orbiting scroll 150, respectively, and a communication groove 151d is recessed by a predetermined depth between the plurality of valve accommodation grooves 151c. Also, a discharge hole 151e may be formed from the valve accommodation groove 151c or the communication groove 151d to the outer circumferential surface of the non-orbiting scroll 150 in a penetrating manner. Even when the valve accommodation grooves 151c, the communication groove 151d and the discharge hole 151e are formed on the rear surface of the disk portion 151 of the non-orbiting scroll 150, the basic construction and operation effects are the same as or similar to those of the aforementioned embodiment. However, as illustrated in this embodiment, when the valve accommodation grooves 151c, the communication groove 151d and the discharge hole 151e are formed on the rear surface of the disk portion 151 of the non-orbiting scroll 150, lengths of the bypass holes 151b may be reduced, thereby reducing a dead volume.

Meanwhile, the scroll compressor continuously operates while a gap between the high pressure portion and the low pressure portion is blocked. When a usage environmental condition for the compressor is changed, temperature of the discharge space of the high pressure portion may increase up to a preset temperature or more. In this instance, some components of the compressor may be damaged due to such high temperature.

Considering this, as illustrated in FIG. 12, an overheat preventing unit 190 may be disposed on the high/low pressure dividing plate 115 according to this embodiment. The overheat preventing unit 190 according to this embodiment may communicate the high pressure portion 112 and the low pressure portion 111 with each other such that a refrigerant of the high pressure portion 112 is leaked into the low pressure portion 111, when temperature of the high pressure portion 112 is raised up to a preset temperature or more. The leaked hot refrigerant arouses an operation of an overload breaker 121b provided on an upper end of the winding coil 121a of the stator 121, thereby stopping the operation of the compressor. Therefore, the overheat preventing unit 190 is preferably configured to be sensitive to temperature of the discharge space.

The overheat preventing unit 190 according to this embodiment may be spaced apart from the high/low pressure dividing plate 115 by a predetermined interval, if possible, taking into account the point that the high/low pressure dividing plate 115 is formed of a thin plate material and divides the high pressure portion 112 and the low pressure portion 111. This may allow the overheat preventing unit 190 to be less affected in view of temperature by the low pressure portion 111 with relatively low temperature.

In more detail, the overheat preventing unit 190 according to this embodiment may be provided with a body 191 which is separately fabricated to accommodate a valve plate 195, and the body 191 may then be coupled to the high/low pressure dividing plate 115. Accordingly, the high/low pressure dividing plate and the valve plate may be spaced apart from each other by a predetermined interval, such that the valve plate can be less affected by the high/low pressure dividing plate.

The body 191 may be made of the same material as the high/low pressure dividing plate 115. However, the body 191 may preferably be made of a material with a low heat transfer rate, in terms of insulation. The body 191 may be provided with a valve accommodating portion 192 having a valve space, and a coupling portion 193 protruding from a center of an outer surface of the valve accommodating portion 192 by a predetermined length and coupling the body 191 to the high/low pressure dividing plate 115.

The valve accommodating portion 192 includes a mounting portion 192a formed in a disk-like shape and having the valve plate 195 mounted on an upper surface thereof, and a side wall portion 192b extending from an edge of the mounting portion 192a into an annular shape and forming the valve space together with an upper surface of the mounting portion 192a. The mounting portion 192a may be thicker than the side wall portion 192b in thickness. However, when the mounting portion is thicker, an effect of holding heat may be generated. Therefore, the thickness of the mounting portion may alternatively be thinner than that of the side wall portion within a range of ensuring reliability.

A stepped surface 192c supported by the high/low pressure dividing plate 115 is formed on a lower surface of the mounting portion 192a. Accordingly, a lower surface of an outer mounting portion 192d which is located outside the stepped surface 192c of the lower surface of the mounting portion 192a may be spaced apart from an upper surface 115c of the high/low pressure dividing plate 115 by a predetermined height (interval) h. This may result in reducing a contact area between the body and the high/low pressure dividing plate and simultaneously enhancing reliability by allowing a refrigerant of the discharge space to be introduced between the body and the high/low pressure dividing plate.

However, an insulating material, such as a gasket 194, which serves as a sealing member, may preferably be provided between the stepped surface 192c and the high/low pressure dividing plate 115, in the aspect of preventing heat transfer between the body 191 and the high/low pressure dividing plate 115.

Also, a communication hole 191a through which the high pressure portion 112 and the low pressure portion 111 communicate with each other is formed from a center of the upper surface of the mounting portion 192a to a lower end of the coupling portion 193. A damper (not illustrated) in which a sealing protrusion 195c of the valve plate 195 is inserted may be formed in a tapering manner on an inlet of the communication hole 191a, namely, an end portion of the upper surface of the mounting portion 192a.

A supporting protrusion 192e is formed on an upper end of the side wall portion 192b. The supporting protrusion 192e is bent after inserting a valve stopper 196 therein, so as to support the valve stopper 196. The valve stopper 196 may be formed in a ring shape with a first gas hole 196a formed at a center thereof to allow a refrigerant of the high pressure portion 112 to always come in contact with a first contact surface 195a of the valve plate 195.

Here, the mounting portion 192a may be provided with at least one second gas hole 192f through which the refrigerant of the high pressure portion 112 always comes in contact with a second contact surface 195b of the valve plate 195. Accordingly, the refrigerant of the discharge space may come in contact directly with the first contact surface 195a of the valve plate 195 through the first gas hole 196a and simultaneously come in contact directly with the second contact surface 195b of the valve plate 195 through the second gas hole 192f. This may result in reducing a temperature difference between the first contact surface 195a and the second contact surface 195b of the valve plate 195 and simultaneously increasing a responding speed of the valve plate 195.

The valve plate 195 may be configured as a bimetal to be thermally transformed according to temperature of the high pressure portion 112 and thereby open and close the communication hole 191a. The sealing protrusion 195c protrudes from a central portion of the valve plate 195 toward the communication hole 191a, and a plurality of refrigerant holes 195d through which the refrigerant flows during an opening operation are formed around the sealing protrusion 195c.

Meanwhile, a thread is formed on an outer circumferential surface of the coupling portion 193 such that the coupling portion 193 can be screw-coupled to a coupling hole 115b provided on the high/low pressure dividing plate 115. However, in some cases, the coupling portion 193 may be press-fitted into the coupling hole 115b or coupled to the coupling hole 115b in a welding manner or by using an adhesive.

The overheat preventing unit of the scroll compressor according to this embodiment may extend a path along which low refrigerant temperature of the low pressure portion 111 is transferred to the valve plate 195 by a heat transfer through the high/low pressure dividing plate 115, which may increase an insulating effect and accordingly allow the valve plate 195 to be much less affected by the temperature of the low pressure portion 111.

On the other hand, the valve plate 195 may be located in the discharge space of the high pressure portion 122 by being spaced apart from the upper surface 115c of the high/low pressure dividing plate 115, adjacent to the high pressure portion 112, by the predetermined height h. Accordingly, the valve plate 195 may be mostly affected by the temperature of the high pressure portion 112, and thus sensitively react with respect to the increase in the temperature of the high pressure portion 112.

Accordingly, when the temperature of the high pressure portion increases up to a set value or more, the valve plate may fast be open and the refrigerant of the high pressure portion may fast flow toward the low pressure portion through the bypass holes. The refrigerant arouses the operation of the overload breaker provided in the driving motor and thereby the compressor is stopped. With the configuration, the overheat preventing unit can correctly react with the operating state of the compressor without distortion, thereby preventing damage on the compressor due to high temperature in advance.

The foregoing embodiments have exemplarily illustrated a low pressure type scroll compressor, but the present invention can be equally applied to any hermetic compressor in which an inner space of a casing is divided into a low pressure portion as a suction space and a high pressure portion as a discharge space.

It should also be understood that the above-described embodiments are not limited by any of the details of the foregoing description, unless otherwise specified, but rather should be construed broadly within its scope as defined in the appended claims, and therefore all changes and modifications that fall within the metes and bounds of the claims, or equivalents of such metes and bounds are therefore intended to be embraced by the appended claims.

Therefore, an aspect of the detailed description is to provide a scroll compressor capable of reducing fabricating costs by simplifying a structure of a capacity varying apparatus.

Another aspect of the detailed description is to provide a scroll compressor capable of relaxing restrictions on components constructing a capacity varying apparatus.

Another aspect of the detailed description is to provide a scroll compressor capable of easily supplying power for operating a capacity varying apparatus.

Another aspect of the detailed description is to provide a scroll compressor capable of enhancing responsiveness by simplifying a control of a capacity varying apparatus.

Another aspect of the detailed description is to provide a scroll compressor capable of preventing in advance efficiency of the compressor from being lowered due to over-compression, by employing a bypass hole and a check valve for opening and closing the bypass hole.

To achieve these and other advantages and in accordance with the purpose of this specification, as embodied and broadly described herein, there is provided a scroll compressor having a high/low pressure dividing plate for dividing an inner space of a casing into a high pressure portion and a low pressure portion, the compressor including a passage formed between a non-orbiting scroll and a back pressure chamber assembly to communicate with an intermediate pressure chamber, and a valve provided at the passage to open and close the passage.

Here, the scroll compressor may further include a check valve disposed at the passage and opened and closed according to a pressure difference of the intermediate pressure chamber.

To achieve these and other advantages and in accordance with the purpose of this specification, as embodied and broadly described herein, there is provided a scroll compressor, comprising: a casing; an orbiting member provided within the casing, and the orbiting member to perform an orbiting motion; a non-orbiting member, wherein the orbiting member and the non-orbiting member to form a compression chamber, the compression chamber having a suction chamber, an intermediate pressure chamber and a discharge chamber; a communication passage configured to communicate inside and outside of the compression chamber; an opening/closing valve assembly configured to open and close the communication passage, the opening/closing valve assembly provided outside the non-orbiting member and within the casing; and a switching valve assembly configured to control the opening/closing valve assembly, the switching valve assembly being provided within the casing.

Here, the opening/closing valve assembly includes a valve to operate based on a pressure difference, and the switching valve assembly includes a valve to be electronically controlled.

Comprising a connection passage provided outside of the non-orbiting member, wherein the opening/closing valve assembly and the switching valve assembly are coupled to each other via the connection passage.

Comprising a connection passage provided within the non-orbiting member, wherein the opening/closing valve assembly and the switching valve assembly are coupled to each other via the connection passage.

The non-orbiting member includes a bypass hole to allow a refrigerant of the intermediate pressure chamber to at least partially pass, and wherein a check valve is provided at the bypass hole to open and close the bypass hole.

The non-orbiting member includes a plurality of bypass holes, and wherein a plurality of check valves are provided at the plurality of bypass holes, respectively, to open and close the corresponding bypass hole.

To achieve these and other advantages and in accordance with the purpose of this specification, as embodied and broadly described herein, there is provided a scroll compressor, comprising: a casing having a hermetic inner space separated into a low pressure portion and a high pressure portion; an orbiting scroll disposed within the inner space of the casing, and the orbiting scroll to perform an orbiting motion; a non-orbiting scroll, wherein the orbiting scroll and the non-orbiting scroll to form a compression chamber, the compression chamber having a suction chamber, an intermediate pressure chamber and a discharge chamber; a back pressure chamber assembly coupled to the non-orbiting scroll to form a back pressure chamber; a bypass hole provided at the intermediate pressure chamber; a check valve at the bypass hole to open and close the bypass hole; a valve accommodation groove formed on at least one of the non-orbiting scroll or the back pressure chamber assembly, wherein the check valve is provided in the valve accommodation groove; a communication passage to provide communication between the valve accommodation groove and the low pressure portion of the casing; a first valve assembly provided on the back pressure chamber assembly or the non-orbiting scroll to selectively open and close the communication passage; and a second valve assembly provided within the casing and coupled to the first valve assembly, the second valve assembly to control opening and closing operations of the first valve assembly such that the first valve assembly opens and closes the communication passage.

Here, comprising a connection pipe provided outside of the non-orbiting scroll or the back pressure chamber assembly, wherein the first valve assembly and the second valve assembly are coupled to each other via the connection pipe.

Comprising a connection passage groove provided on the non-orbiting scroll or the back pressure chamber assembly, wherein the first valve assembly and the second valve assembly are coupled to each other via the connection passage groove.

The first valve assembly comprises: a valve guide having a valve space to provide communication with the communication passage, an exhaust hole to provide communication between the valve space and the low pressure portion, a differential pressure space formed at one side of the valve space, and an injection hole to provide communication between the differential pressure space and the second valve assembly such that pressure is applied to the differential pressure space; and a valve at the valve space to open and close the communication passage based on pressure at the differential pressure space.

The second valve assembly comprises: a multifold part having a plurality of passages coupled to the back pressure chamber, the low pressure portion of the casing and the first valve assembly, respectively; and a valve part selectively connecting each passage of the multifold part to change a flow direction of a refrigerant.

The bypass hole includes a plurality of bypass holes, and the check valve includes a plurality of check valves to independently open and close the plurality of bypass holes, respectively.

The valve accommodation groove includes a plurality of valve accommodation grooves, wherein the plurality of check valves are provided at the plurality of valve accommodation grooves, respectively, and wherein a communication groove is provided between two of the plurality of valve accommodation grooves.

To achieve these and other advantages and in accordance with the purpose of this specification, as embodied and broadly described herein, there is provided a scroll compressor, comprising: a casing; a driving motor within an inner space of the casing; a high/low pressure dividing plate attached to the driving motor to separate the inner space of the casing into a low pressure portion and a high pressure portion; a main frame spaced from the high/low pressure dividing plate; an orbiting scroll at the main frame to perform an orbiting motion based on the driving motor; a non-orbiting scroll to move up and down with respect to the orbiting scroll, and the non-orbiting scroll to form, along with the orbiting scroll, a suction chamber, an intermediate pressure chamber and a discharge chamber; a back pressure plate attached to the non-orbiting scroll, and the back pressure plate having a space portion to communicate with the intermediate pressure chamber and having an open surface to face the high/low pressure dividing plate; and a floating plate movably coupled to the back pressure plate to hermetically seal the space portion so as to form a back pressure chamber, wherein the non-orbiting scroll includes: a plurality of bypass holes formed from the intermediate pressure chamber to a surface of the non-orbiting scroll to face the back pressure plate, and check valves at the surface of the non-orbiting scroll for opening and closing the bypass holes, respectively, wherein a communication groove is provided on at least one of the surface of the non-orbiting scroll or surface of the back pressure plate corresponding to the surface of the non-orbiting scroll, wherein a discharge hole to communicate between the communication groove and the low pressure portion is provided at one of the non-orbiting scroll or the back pressure plate, wherein a first valve assembly is to selectively open and close the discharge hole to selectively communicate between the intermediate pressure chamber and the low pressure portion, wherein the first valve assembly is provided on a surface of the non-orbiting scroll or the back pressure plate, and wherein a second valve assembly is provided within the casing, the second valve assembly is to operate based on an external power source to generate differential pressure in the first valve assembly such that the first valve assembly selectively opens and closes the discharge hole.

Here, the casing is provided with two terminals.

A first one of the two terminals is electrically connected to the driving motor, and a second one of the two terminals is electrically connected to the second valve assembly.

The second valve assembly is coupled to an outer circumferential surface of the non-orbiting scroll or the back pressure plate.

Comprising a connection pipe provided outside the non-orbiting scroll or the back pressure plate, wherein the first valve assembly and the second valve assembly are coupled to each other via the connection pipe.

Comprising a connection passage groove on the non-orbiting scroll or the back pressure chamber assembly, wherein the first valve assembly and the second valve assembly are coupled to each other via the connection passage groove.

An overheat preventing device is provided on the high/low pressure dividing plate, and wherein the overheat preventing device has a portion accommodating a valve, the portion being spaced from the high/low pressure dividing plate.

A scroll compressor according to the present invention may use a less number of components by virtue of installing a check valve in a bypass hole and also simplify a bypass passage for bypassing a refrigerant by virtue of installing a control valve at the bypass hole. This may result in facilitating fabrication of a capacity varying apparatus.

As a control valve is installed at a passage, a refrigerant may be in a state of being already arrived at an outlet of the passage when switching a power operation mode into a saving operation mode, which may allow for fast switching into the saving operation mode.

Also, a position of a control valve may be changed by using a communication pipe, and thus restriction on a specification of the control valve can be relaxed. This may result in enhancing reliability of a capacity varying apparatus.

A bypass hole for bypassing a part of a compressed refrigerant within an intermediate pressure chamber and a check valve for opening and closing the bypass hole can be installed, thereby preventing in advance degradation of efficiency of the compressor due to over-compression.

In addition, as both of a first valve assembly and a second valve assembly provided for varying a capacity may be disposed outside a non-orbiting scroll or a back pressure plate which is a compression unit, the first valve assembly can be simplified in structure and reduced in size. Accordingly, the second valve assembly controlling the first valve assembly can also be reduced in size.

Further scope of applicability of the present application will become more apparent from the detailed description given hereinafter. However, it should be understood that the detailed description and specific examples, while indicating preferred embodiments of the invention, are given by way of illustration only, since various changes and modifications within the spirit and scope of the invention will become apparent to those skilled in the art from the detailed description.

Any reference in this specification to “one embodiment,” “an embodiment,” “example embodiment,” etc., means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment. The appearances of such phrases in various places in the specification are not necessarily all referring to the same embodiment. Further, when a particular feature, structure, or characteristic is described in connection with any embodiment, it is submitted that it is within the purview of one skilled in the art to affect such feature, structure, or characteristic in connection with other ones of the embodiments.

Although embodiments have been described with reference to a number of illustrative embodiments thereof, it should be understood that numerous other modifications and embodiments can be devised by those skilled in the art that will fall within the spirit and scope of the principles of this disclosure. More particularly, various variations and modifications are possible in the component parts and/or arrangements of the subject combination arrangement within the scope of the disclosure, the drawings and the appended claims. In addition to variations and modifications in the component parts and/or arrangements, alternative uses will also be apparent to those skilled in the art.

	Number	Date	Country
Parent	15390246	Dec 2016	US
Child	16397490		US

SCROLL COMPRESSOR

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