KR20190036295A - A screw compressor and a Chiller system including the same - Google Patents

Abstract

The present invention relates to a screw compressor and a chiller system including the same. According to an idea of the present invention, the screw compressor comprises: a rotary shaft; a motor assembly for providing a driving force to the rotary shaft; a rotor compressing a refrigerant while rotating in the axial direction by the rotary shaft; and a slide valve disposed on one side of the rotor to change refrigerator capacity. Moreover, the slide valve is installed to rotate in the axial direction.

Description

[0001] The present invention relates to a screw compressor and a chiller system including the same,

The present invention relates to a screw compressor and a chiller system including the same.

Generally, a chiller system refers to a system that supplies cold water to a customer. Specifically, the chiller system is characterized in that the cold water is cooled by heat exchange between the refrigerant circulating in the refrigerant cycle and the cold water circulating the customer. In addition, the chiller system is a relatively large-capacity facility and can be installed in a large-scale building or the like.

The chiller system includes a chiller unit and a demander. The demander may be understood as an air conditioner using cold water as an example.

The chiller unit includes a compressor for compressing the refrigerant, a condenser for condensing the refrigerant compressed in the compressor, an expansion device for decompressing the refrigerant condensed in the condenser, and an evaporator for evaporating the refrigerant decompressed in the expansion device . The refrigerant is heat-exchanged with the outside air in the condenser, and can be heat-exchanged with the cold water in the evaporator.

The chiller unit may be provided in various sizes or capacities. Here, the size or the capacity of the chiller unit may be expressed in units of a freezing tone (RT) as a concept corresponding to the capability of the refrigeration system, that is, the refrigeration capacity.

The chiller unit may be equipped with various refrigeration tones according to the size of a building or the like on which the chiller unit is installed, the capacity of circulating cold water, the air conditioning capacity, or the like. For example, the chiller unit may have a capacity of 200RT, 500RT, 1000RT, 1500RT, 2000RT, 3000RT, or the like.

Various types of compressors such as centrifugal compressors and screw compressors may be used for the chiller unit. The screw compressor includes a pair of screws composed of a male screw and a female screw, thereby compressing the refrigerant.

With regard to the construction of the screw compressor, the following prior art documents have been disclosed.

[Prior Art]

1. Patent No. 10-0350839, a refrigeration screw compressor having a gas operated slide valve

This prior art document discloses a slide valve for varying the capacity of a compressor. At this time, the slide valve linearly moves parallel to the axial direction of the screw using the oil pressure of the oil.

Since such a slide valve has a very complicated structure, the manufacturing process is increased and the price is increased. In addition, since it is difficult to grasp the exact position of the slide valve, it is difficult to control the slide valve to the required capacity.

The present invention provides a screw compressor having a slide valve that is directly connected to a motor and rotates and accurately grasps the rotational position, and a chiller system including the screw compressor.

Further, there is provided a screw compressor provided with a slide valve that is simple in structure and does not require additional control, and a chiller system including the screw compressor.

The screw compressor according to the present invention includes a rotary shaft, a motor assembly for applying a driving force to the rotary shaft, a rotor rotating about the axial direction by the rotary shaft and compressing the refrigerant, And a slide valve disposed on one side, wherein the slide valve is installed to be rotated about the axial direction.

The slide valve may further include a slide motor attached to one side of the slide valve to apply a driving force to the slide valve so that the slide valve is rotated about the axial direction.

The slide motor may be provided to measure a rotation angle of the slide valve.

A compression bypass groove recessed in the radial direction may be formed in the slide valve.

The compression bypass groove may be formed such that the depression volume is changed along the periphery of the slide valve.

The compression bypass groove may be formed to have a different shape as viewed from one side as the slide valve is rotated.

The slide valve may be formed in a cylindrical shape, and the compression bypass groove may be recessed radially inwardly in a triangular shape.

The rotor may include a first rotor and a second rotor that rotate in mesh with each other, and the first rotor, the second rotor, and the slide valve may be rotated about a rotation axis provided parallel to each other .

The first rotor and the second rotor may be arranged in parallel so that at least a part thereof is in contact with each other, and the slide valve may be disposed on a side between the first rotor and the second rotor.

Wherein the first rotor, the second rotor, and the slide valve are accommodated in the compression chamber, wherein the compression chamber includes a first accommodating portion in which the first rotator is accommodated, 2 accommodating portion, a third accommodating portion accommodating the slide valve, and a compression bypass plate formed between the first accommodating portion, the second accommodating portion, and the third accommodating portion.

A plurality of bypass holes spaced in the axial direction may be formed in the compression bypass plate.

As the slide valve is rotated, the refrigerant can flow through a different number of bypass holes.

The slide valve is provided so as to be in contact with one side of the compression bypass plate. As the slide valve is rotated, an area of contact between the slide valve and the compression bypass plate may be changed.

The compression bypass plate may have a triangular cross section and may extend in the axial direction so as to correspond to the first accommodating portion, the second accommodating portion, and the third accommodating portion.

The chiller system according to the present invention includes the screw compressor described above.

According to the present invention, it is possible to provide a screw compressor capable of varying the capacity through a slide valve having a simple structure.

In particular, the slide valve is provided in a configuration rotated by a slide motor provided separately, and has a very simple structure, so that the manufacturing time and installation time can be reduced.

In addition, since the slide valve is provided with a simple structure and a separate power source is provided, the internal structure of the screw compressor is simplified.

Further, the slide valve is directly connected to the slide motor and can be rotated accurately to the input value as it rotates, and there is an advantage that no additional configuration is required.

In addition, the slide motor has an advantage in that the accurate position of the slide valve can be easily grasped by measuring the rotation angle of the slide valve, and the capacity variable amount can be easily and accurately known.

In addition, the slide valve has a compression bypass groove having a different volume along the periphery, so that the amount of refrigerant bypassed can be easily controlled.

Further, it is possible to provide a compression bypass plate between the slide valve and the rotor for compressing the refrigerant, and it is possible to prevent the refrigerant from suddenly flowing by the plurality of compression bypass holes formed in the compression bypass plate .

1 is a diagram illustrating a chiller system according to an embodiment of the present invention.
FIG. 2 is a view schematically showing a configuration of a chiller unit according to an embodiment of the present invention.
3 is a view conceptually showing the chiller unit of FIG. 2 together with the flow of the refrigerant.
4 is a schematic cross-sectional view of a screw compressor according to an embodiment of the present invention.
5 is a partially exploded view of a screw compressor according to an embodiment of the present invention.
6 is a view showing a slide valve of a screw compressor according to an embodiment of the present invention.
7 is a view schematically showing the operation of a slide valve of a screw compressor according to an embodiment of the present invention.

Hereinafter, some embodiments of the present invention will be described in detail with reference to exemplary drawings. It should be noted that, in adding reference numerals to the constituent elements of the drawings, the same constituent elements are denoted by the same reference symbols as possible even if they are shown in different drawings. In the following description of the embodiments of the present invention, a detailed description of known functions and configurations incorporated herein will be omitted when it may make the difference that the embodiments of the present invention are not conclusive.

In describing the components of the embodiment of the present invention, terms such as first, second, A, B, (a), and (b) may be used. These terms are intended to distinguish the constituent elements from other constituent elements, and the terms do not limit the nature, order or order of the constituent elements. When a component is described as being "connected", "coupled", or "connected" to another component, the component may be directly connected or connected to the other component, Quot; may be "connected," "coupled," or "connected. &Quot;

1 is a diagram illustrating a chiller system according to an embodiment of the present invention.

1, a chiller system 10 according to an embodiment of the present invention includes a chiller unit 100 in which a refrigeration cycle is formed, a cooling tower 20 for supplying cooling water to the chiller unit 100, And a cold water consumer 30 through which cold water to be heat-exchanged with the chiller unit 100 circulates.

At this time, the cold water consumer 30 may be understood as a device or a space for performing air conditioning using cold water.

Between the chiller unit (100) and the cooling tower (20), a cooling water circulating flow path (40) is provided. The cooling water circulating passage 40 is a pipe for guiding cooling water circulating between the cooling tower 20 and the chiller unit 100.

The cooling water circulating flow path 40 is provided with a cooling water intake flow path 42 for guiding the cooling water to flow into the chiller unit 100 and a cooling water supply path 42 for guiding the cooling water heated by the chiller unit 100 to the cooling tower 20 And a cooling water outflow channel 44 may be included.

A cooling water pump 46 driven for the cooling water may be provided in at least one of the cooling water intake flow path 42 and the cooling water outflow flow path 44. For example, FIG. 1 shows that the coolant pump 46 is provided in the coolant intake passage 42.

The cooling water outflow channel 44 may be provided with an outflow temperature sensor 47 for sensing the temperature of the cooling water flowing into the cooling tower 20. The cooling water intake flow path 42 may be provided with an intake temperature sensor 48 for sensing the temperature of the cooling water discharged from the cooling tower 20.

A cold water circulating passage (50) is provided between the chiller unit (100) and the cold water consumer (30). The cold water circulating passage 50 is a pipe for guiding the cold water to circulate the cold water consumer 30 and the chiller unit 100.

The cold water circulation flow path 50 is provided with a cold water intake flow path 52 for guiding the cold water into the chiller unit 100 and a cold water supply flow path 52 for guiding the cold water cooled in the chiller unit 100 to the cold water consumer 30 A cold water outflow channel 54 may be included.

A cold water pump (56) driven for the flow of cold water may be provided in at least one of the cold water inlet flow path (52) and the cold water outlet flow path (54). For example, FIG. 1 shows that the cold water supply passage 52 is provided with the cold water pump 56.

At this time, the cold water consumer 30 may be a water-cooled air conditioner for exchanging air with cold water.

For example, the cold water consumer 30 may include an air handling unit (AHU) that mixes indoor air and outdoor air and then discharges the mixed air into the indoor space by exchanging heat with cold water, A fan coil unit (FCU) that discharges heat into the room after exchanging heat with cold water, and a bottom piping unit embedded in the floor of the room.

1, the cold water consumer 30 is shown as an air handling unit.

The cold water consumer 30 constituted by the air handling unit is provided with a casing 61 and a cold water coil 62 provided inside the casing 61 through which cold water passes and provided on both sides of the cold water coil 62 And air blowers 63 and 64 for blowing indoor air and outdoor air into the room.

The blowers 63 and 64 are provided with a first blower 63 for allowing indoor air and outdoor air to be sucked into the casing 61 and a second blower 63 for blowing out air to the outside of the casing 61 A blower 64 may be included.

The indoor air suction unit 65, the indoor air discharge unit 66, the ambient air suction unit 67, and the air conditioning air discharge unit 68 may be formed in the casing 61.

When the blowers 63 and 64 are driven, a part of the air sucked into the indoor air suction unit 65 from the room is discharged to the indoor air discharge unit 66 and discharged to the indoor air discharge unit 66 And is mixed with the outdoor air sucked into the outside air suction part (67) and exchanges heat with the cold water coil (62).

The mixed air that has been exchanged (cooled) with the cold water coil 62 can be discharged to the room through the air conditioning air discharge unit 68. Through this process, the indoor space can be cooled by supplying conditioned air.

Further, the cold water consumer 30 may correspond to a facility that uses cold water directly. For example, the cold water consumer 30 may provide cold water for lowering the temperature of the semiconductor component.

In addition, the chiller system 10 according to the present invention can supply cooling water to a hot water consumer other than the cooling tower 20.

That is, the chiller system 10 according to an embodiment of the present invention is not limited to the configuration shown in FIG. 2, and may have various configurations. Hereinafter, the chiller unit 100 connected to the cooling water circulation passage 40 and the cold water circulation passage 50 will be described in detail.

FIG. 2 is a view schematically showing a configuration of a chiller unit according to an embodiment of the present invention.

2, the chiller unit 100 according to an embodiment of the present invention includes a compressor 200, the evaporator 150, and the condenser 140. As shown in FIG.

The compressor 200 is a component for compressing the refrigerant. The compressor 200 according to an embodiment of the present invention is provided with a screw compressor. The screw compressor is understood to be a compressor in which refrigerant is compressed and discharged by engagement of a female screw and a male screw to be rotated. The compressor 200 will be described later in detail.

The condenser 140 is configured such that the refrigerant discharged from the compressor 200 and the cooling water flowing through the cooling water circulation passage 40 are heat-exchanged. That is, the refrigerant compressed from the compressor 200 may be introduced into the condenser 140.

The evaporator 150 is configured such that the refrigerant discharged from the condenser 140 and the cold water flowing through the cold water circulation passage 50 are heat-exchanged. An expansion device 110 (see FIG. 3) is provided between the condenser 140 and the evaporator 150 so that the refrigerant discharged from the condenser 140 is expanded and flows to the evaporator 150.

Referring to FIG. 2, the condenser 140 and the evaporator 150 are installed on the bottom surface, and the compressor 200 is installed on the condenser 140 and the evaporator 150. Such an arrangement is exemplary and the compressor 200, the evaporator 150 and the condenser 140 may be arranged in various ways.

The condenser 140 and the evaporator 150 are provided with a condenser main body 170 and an evaporator main body 180 which are provided in a cylindrical shape extending in the axial direction. The condenser main body 170 and the evaporator main body 180 are provided to have the same axial length and may be installed to be spaced apart from each other by a predetermined distance in the vertical direction. In particular, the condenser main body 170 and the evaporator main body 180 may be installed so that the bottom surface and the axial direction are parallel to each other.

Plates 172 and 182 are attached to both ends of the condenser main body 170 and the evaporator main body 180, respectively. The plates 172 and 182 may have a rectangular shape and may be installed perpendicular to the bottom surface. The plates 172 and 182 include a condensation plate 172 installed in the condenser main body 170 and an evaporation plate 182 installed in the evaporator main body 180.

The condensation plate 172 and the evaporation plate 182 may be combined with legs 171 and 181 provided on the bottom surface so as to be stably installed on the bottom surface. Further, the condensation plate 172 and the evaporation plate 182 are coupled so that one surface thereof is in contact with the other. At this time, each of the joints may be coupled through a coupling member such as a bolt, or may be coupled by welding or the like.

The condensing plate 172 and the evaporation plate 182 are provided with a cooling water receiving portion 174 and a cold water receiving portion 184 for receiving cooling water and cold water.

The condenser plate 172 is coupled to both ends of the condenser main body 170 and the cooling water accommodating portions 174 are coupled to the outside of the condenser plate 172, .

The evaporator 150 is connected to the evaporator plate 182 at both ends of the evaporator body 180 and the cold water receiver 184 is coupled to the outside of the evaporator plate 182 .

The cooling water receiving portion 174 and the cold water receiving portion 184 are provided with cooling water coupling portions 176 and 177 and cold water coupling portions 186 and 187 which are coupled to the cooling water circulation passage 40 and the cold water circulation passage 50, ).

In detail, the cooling water accommodating portion 174 is provided with a first cooling water engaging portion 176 coupled with the cooling water intake flow passage 42 and a second cooling water engaging portion 177 coupled with the cooling water outflow passage 44 . The cold water receiver 184 includes a first cold water coupler 186 coupled to the cold water inlet passage 52 and a second cold water coupler 187 coupled to the cold water outlet flow passage 54 Be able to

2, the first cold water coupling unit 186, the second cold water coupling unit 187, the first cooling water coupling unit 176, and the second cooling water coupling unit 187 are arranged in the vertical direction . However, such an arrangement is understood to be illustrative.

In addition, the chiller unit 100 according to an embodiment of the present invention may include a control box 160 provided with a device capable of controlling each configuration. The control box 160 may be attached in a box shape to one side of the condenser 140 and the evaporator 150. The control box 160 may include a display panel 162 to allow the user to know the operating state of the chiller unit 100.

Hereinafter, the flow of the refrigerant in the chiller unit 100 will be described in detail based on such a structure.

3 is a view conceptually showing the chiller unit of FIG. 2 together with the flow of the refrigerant. 3, the flow of the refrigerant is schematically shown through the refrigerant pipe, and the flow of the cold water and the cooling water in the evaporator 150 and the condenser 140 is schematically shown.

As shown in FIG. 3, the refrigerant compressed in the compressor 200 flows to the condenser 140.

The refrigerant discharged from the compressor (200) is heat-exchanged with the cooling water in the condenser (140). In detail, the refrigerant flowing in the compressor 200 is introduced into the condenser main body 170, and is heat-exchanged with each other while being in contact with the cooling water flowing through the plurality of cooling water pipes 175 provided inside the condenser main body 170 .

The refrigerant heat-exchanged with the cooling water in the condenser 140 passes through the expansion device 110 and flows to the evaporator 150. An economizer may be further provided between the condenser 140 and the evaporator 150 to separate the refrigerant gas generated from the refrigerant discharged from the condenser 140.

At this time, the refrigerant gas separated from the economizer flows into the compressor 200, and the refrigerant liquid can flow to the evaporator 150. At this time, the economizer and the expansion device 110 may be provided in various numbers and disposed at various places. For example, the expansion device 110 may be installed on the suction side and the discharge side of the economizer.

The refrigerant flowing into the evaporator 150 is heat-exchanged with the cold water in the evaporator 150. Specifically, the refrigerant is introduced into the evaporator main body 180, and a plurality of cold water pipes 185 provided in the evaporator main body 180 are exchanged with each other while being in contact with the cold cold water.

The refrigerant evaporated by heat exchange with cold water flows to the compressor (200), and can be circulated as described above.

Hereinafter, the compressor 200 for compressing the refrigerant will be described in detail.

4 is a schematic cross-sectional view of a screw compressor according to an embodiment of the present invention.

As shown in FIG. 4, the compressor 200 according to the present invention includes a casing 201 that forms an internal space. The casing 201 has a substantially cylindrical shape and can be arranged in a lateral direction or in an axial direction.

4, the casing 201 may be elongated in the transverse direction and may have a somewhat lower height in the radial direction. That is, since the compressor 20 can have a low height, when the compressor 20 is installed in the chiller unit 100 described above, the height of the chiller unit 100 can be reduced.

The casing 201 has a refrigerant inlet port 202 and a refrigerant outlet port 204, and may be provided to seal the internal space. The refrigerant inlet port 202 and the refrigerant outlet port 204 may be connected to a refrigerant pipe through which refrigerant flows.

At this time, a refrigerant pipe connected to the evaporator 150 is installed in the refrigerant inlet port 202 so that the refrigerant passing through the evaporator 150 flows into the internal space of the casing 201. The refrigerant inlet 202 may be provided with an inlet filter 202a.

A refrigerant pipe connected to the condenser 140 is installed in the refrigerant discharge port 204 so that the compressed refrigerant flows to the condenser 140.

The casing 201 is provided with a rotor 210, a rotating shaft 220 for rotating the rotor 210, and a motor assembly 230 for applying a driving force to the rotating shaft 220. Referring to FIG. 4, the rotor 210 is disposed on one side of the rotation shaft 220, and the motor assembly 230 is disposed on the other side.

The motor assembly 230 includes a rotor 232 disposed radially outward of the rotation shaft 220 and a stator 234 disposed radially outward of the rotor 232. The rotating shaft 220 can be rotated by an electromagnetic force between the rotor 232 and the stator 234. [

The rotation shaft 220 is rotated by the motor assembly 230 and the rotation shaft 220 can rotate the rotor 210. The first rotor 212 and the second rotor 214 are provided in the rotor 210 and the first rotor 212 is directly connected to the rotating shaft 220 .

Either one of the first rotor 212 and the second rotor 214 may be a male screw and the other may be a female screw. That is, the rotor 210 can be understood as a pair of screws that mesh with each other.

In summary, power is applied to the motor assembly 230 to rotate the rotation shaft 220, and the first rotor 212 connected to the rotation shaft 220 is rotated. Further, the second rotor 214 engaged with the first rotor 212 is rotated. For convenience of explanation, the first rotor 212 is shown as a male screw, but the present invention is not limited thereto.

The first rotor 212 and the second rotor 214 may be accommodated in a compression chamber 216 formed in the casing 201. The compression chambers 216 are provided with openings through which coolant flows in and out. Accordingly, the refrigerant flowing into the compression chamber 216 is compressed and discharged in a space defined by the first rotor 212 and the second rotor 214.

Specifically, the first rotor 212 and the second rotor 214 are engaged so as to rotate toward each other. Accordingly, when the first rotor 212 and the second rotor 214 are rotated, the fluid between the first rotor 212 and the second rotor 214 can be compressed by reducing the volume therebetween.

The compression chamber 216 may be provided with various devices such as a first rotor 212 and a supporter 218 mounted on one end of the second rotor 214.

In addition, various configurations for oil for lubricating the driving unit may be provided in the casing 201. For example, an oil filter 205 may be provided on one side of the casing 201.

The compressor 200 according to an embodiment of the present invention may be provided with a slide valve 300 for regulating the pressure of the refrigerant. That is, the slide valve 300 corresponds to a structure for adjusting the capacity of the compressor 200. Hereinafter, this will be described in detail.

5 is a partially exploded view of a screw compressor according to an embodiment of the present invention. 5 is an exploded perspective view of the compression chamber 216. As shown in FIG. For convenience of explanation, only necessary configurations are shown.

As shown in FIG. 5, the compression chamber 216 is provided with an internal space in which the first rotor 212 and the second rotor 214 are accommodated. Hereinafter, a space in which the first rotors 212 are accommodated is referred to as a first accommodating portion 212a, and a space in which the second rotors 214 are accommodated is referred to as a second accommodating portion 214a.

The compression chamber 216 is provided with an internal space in which the slide valve 300 is received. Hereinafter, the space in which the slide valve 300 is accommodated is referred to as a third accommodating portion 300a.

5, the first receiving portion 212a, the second receiving portion 214a, and the third receiving portion 300a extend in the axial direction and are provided in parallel to each other. The first accommodating portion 212a and the second accommodating portion 214a are arranged in parallel in the radial direction and the third accommodating portion 300a is disposed between the first accommodating portion 212a and the second accommodating portion 214a, And is disposed on the upper side of the portion 214a.

The third accommodating portion 300a is disposed between the first accommodating portion 212a and the second accommodating portion 214a. That is, the first receiving portion 212a, the second receiving portion 214a, and the third receiving portion 300a may be arranged in a substantially triangular shape in the radial direction.

In correspondence with this shape, the first rotor 212, the second rotor 214, and the slide valve 300 are provided so as to extend in the axial direction and rotate. The first rotor 212, the second rotor 214, and the slide valve 300 may be arranged in a substantially triangular shape in the radial direction.

In other words, the slide valve 300 is rotatably provided in the axial direction. Referring to FIG. 4, the slide valve 300 may be connected to the slide motor 310 and rotated. The slide motor 310 may be disposed on one side of the compression chamber 216 and connected to the slide valve 300.

The slide motor 310 may be equipped with a step motor or the like capable of measuring the amount of rotation. That is, the slide motor 310 is provided to detect the rotation angle of the slide valve 300 according to driving. However, this is an exemplary one, and the slide valve 300 may be rotatably disposed using various driving forces.

The slide valve 300 may have a substantially cylindrical shape. Also, as described above, the first rotor 212 and the second rotor 214 are formed of screws and have an outer shape substantially cylindrical. Accordingly, a substantially triangular space is formed between the first rotor 212, the second rotor 214, and the slide valve 300.

The compression chamber 216 is provided with a compression bypass plate 218 corresponding to the space. Therefore, the compression bypass plate 218 has a substantially triangular cross section corresponding to the space between the first rotor 212, the second rotor 214, and the slide valve 300. The compression bypass plate 218 extends in the axial direction to a size corresponding to the first rotor 212, the second rotor 214, and the slide valve 300.

Referring to FIG. 5, the compression chamber 216 is provided with a detachable compression chamber cover 216a. This is an exemplary shape and the compression chamber 216 can be integrally formed.

As described above, the compression chamber 216 includes the first accommodating portion 212a in which the first rotator 212, the second rotator 214, and the slide valve 300 are accommodated, 2 accommodating portion 214a and the third accommodating portion 300a. The compression bypass plate 218 is provided between the first accommodating portion 212a, the second accommodating portion 214a, and the third accommodating portion 300a.

The compression bypass plate 218 is provided with a plurality of compression bypass holes 219 (see FIG. 7) spaced in the axial direction. The compression bypass hole 219 is provided so that the refrigerant can flow through the first accommodating portion 212a, the second accommodating portion 214a, and the third accommodating portion 300a.

Hereinafter, the shape of the slide valve 300 will be described in detail.

6 is a view showing a slide valve of a screw compressor according to an embodiment of the present invention.

As shown in FIG. 6, the slide valve 300 is generally formed in a cylindrical shape. When the overall shape of the slide valve 300 is defined, it corresponds to a cylindrical shape having a length A in the axial direction and a radius B.

At this time, the slide valve 300 is provided with a compression bypass groove 302. The compression bypass groove (302) is provided in a shape recessed radially inward from the overall shape of the slide valve (300).

Particularly, the compression bypass groove 302 is formed to vary the depression volume along the periphery of the slide valve 300. That is, the compression bypass groove 302 may be formed to have different shapes as seen from one side as the slide valve 300 is rotated.

For example, the compression bypass groove 302 is recessed to a predetermined depth, and at least a part of the slide valve 300 is provided to have a radius b smaller than B. [ In FIG. 6, the compression bypass grooves 302 are depressed to the same depth, but this is merely an example. That is, the compression bypass grooves 302 may be recessed to different depths.

Further, the compression bypass groove 302 may be recessed in a length a smaller than A in the lateral direction. However, a may have a length greater than half the length of A. In this case, 'a' refers to the maximum axial length of the compression bypass groove 302.

In addition, the compression bypass groove 302 is inclined from one end of the slide valve 300 to a point having a length a in the axial direction. Referring to FIG. 6, the compression bypass groove 302 is formed to have a circumferential length of c at one end of the slide valve 300.

In summary, the compression bypass groove 302 is recessed at a predetermined depth in the radial direction of the slide valve 300, and is formed to have a length c and a maximum axial length a in the circumferential direction. The compression bypass groove 302 is recessed in the slide valve 300 in a substantially triangular shape.

At this time, the compression bypass groove 302 has a circumferential length c and an axial length a, and has an inclined path connecting the circumferential length c and the axial length a. The inclined path may be provided at an inclined angle that gives the same amount of change according to the rotation angle when the slide valve 300 is rotated. That is, when the slide valve 300 is rotated, the volume of the depressed portion by the compression bypass groove 302 may be changed equally.

The variable capacity of the refrigerant through the structure of the slide valve 300 will be described below.

 7 is a view schematically showing the operation of a slide valve of a screw compressor according to an embodiment of the present invention. 7 is a cross-sectional view of the slide valve 300, and the second rotor 214 is omitted.

As shown in FIG. 7, the slide valve 300 is provided above the first rotor 212. However, this is merely exemplary and it is sufficient that the slide valve 300 is disposed on the side between the first rotor 212 and the second rotor 214.

The compression bypass plate 218 is disposed between the first rotor 212 and the second rotor 214 and the slide valve 300. As described above, the compression bypass plate 218 is provided with a plurality of compression bypass holes 219 spaced in the axial direction.

At this time, one side of the slide valve 300 may be disposed in contact with the compression bypass plate 218. It does not mean that 'touching' is completely close, but it can be understood that the refrigerant is arranged at such a distance that the refrigerant can not flow.

Referring to FIG. 7 (a), one side of the slide valve 300 is disposed so as to be in contact with the compression bypass plate 218 as a whole. In detail, the slide valve 300 is disposed in a state rotated so that the compression bypass plate 218 and the compression bypass groove 302 are not adjacent to each other.

When the slide valve 300 is disposed in this manner, the refrigerant does not flow through the compression bypass hole 219. That is, the refrigerant may not flow into the third accommodating portion 300a.

Referring to FIG. 7 (b), one side of the slide valve 300 is disposed in partial contact with the compression bypass plate 218. In detail, the slide valve 300 is disposed so that at least a part of the compression bypass plate 218 and the compression bypass groove 302 are adjacent to each other.

At this time, the compression bypass hole (302) allows the refrigerant to flow through the compression bypass hole (219). That is, the refrigerant can flow into the third accommodating portion 300a. Thereby, the space in which the refrigerant flows in the compression chamber 216 is increased, and the flow rate of the refrigerant can be increased.

7 (c), one side of the slide valve 300 is disposed in contact with the compression bypass plate 218 with a smaller area than that of FIG. 7 (b). In detail, the slide valve 300 is disposed in a state rotated so that the compression bypass plate 218 and the compression bypass groove 302 having a larger axial length are adjacent to each other.

For example, the portion having the maximum axial length of the compression bypass groove 302 may be disposed adjacent to the compression bypass plate 218.

At this time, more refrigerant can be introduced through the compression bypass hole 219 by the compression bypass groove 302. That is, as the axial length of the compression bypass groove 302 is increased, more compression bypass holes 219 are opened and more refrigerant flows.

As the slide valve 300 is rotated, the arrangement of the compression bypass plate 218 and the compression bypass groove 302 becomes different. Accordingly, the compression bypass holes 219 are opened to different numbers and the amount of refrigerant introduced into the compression bypass holes 219 can be increased or decreased.

That is, as the slide valve 300 rotates, the refrigerant can flow through the different number of bypass holes 219. The screw compressor according to claim 1, wherein an area of the slide valve (300) contacting the compression bypass plate (218) is changed as the slide valve (300) is rotated.

Further, as described above, the rotation angle of the slide valve 300 can be detected by the slide motor 310. Accordingly, the arrangement of the compression bypass groove 302 can be known, and the amount of the refrigerant introduced can be easily known. That is, the amount of the variable refrigerant can be easily known through the rotation angle of the slide valve 300.

10: Chiller system 100: Chiller unit
110: expansion device 140: condenser
150: Evaporator 200: Compressor
210: rotor 212: first rotor
214: second rotor 316: compression bypass plate
318: Compression bypass hole 320:
300: Slide valve

Claims (15)

A rotating shaft;
A motor assembly for applying a driving force to the rotary shaft;
A rotor rotated around the axial direction by the rotary shaft and compressing the refrigerant; And
And a slide valve disposed on one side of the rotor to vary the capacity of the refrigerant,
Wherein the slide valve is installed to rotate about the axial direction. The method according to claim 1,
Further comprising a slide motor attached to one side of the slide valve to apply a driving force to the slide valve so that the slide valve is rotated about the axial direction. 3. The method of claim 2,
Wherein the slide motor is provided to measure a rotation angle of the slide valve. The method according to claim 1,
And a compression bypass groove recessed in the radial direction is formed in the slide valve. 5. The method of claim 4,
Wherein the compression bypass groove is provided so that the recessed volume is changed along the circumference of the slide valve. 5. The method of claim 4,
Wherein the compression bypass groove is formed to have a different shape as viewed from one side as the slide valve is rotated. 5. The method of claim 4,
Wherein the slide valve is provided in a cylindrical shape,
Wherein the compression bypass grooves are recessed radially inwardly in a triangular shape. The method according to claim 1,
Wherein the rotor includes a first rotor and a second rotor that are meshed and rotated with each other,
Wherein the first rotor, the second rotor, and the slide valve are rotated about a rotation axis provided parallel to each other. 9. The method of claim 8,
Wherein the first rotor and the second rotor are arranged so as to be at least partially in contact with each other,
And the slide valve is disposed on a side between the first rotor and the second rotor. 9. The method of claim 8,
Further comprising a compression chamber in which the first rotor, the second rotor, and the slide valve are accommodated,
In the compression chamber,
A first receiving portion in which the first rotor is accommodated;
A second accommodating portion in which the second rotator is accommodated;
A third accommodating portion in which the slide valve is accommodated; And
And a compression bypass plate formed between the first accommodating portion, the second accommodating portion, and the third accommodating portion. 11. The method of claim 10,
And a plurality of bypass holes spaced in the axial direction are formed in the compression bypass plate. 12. The method of claim 11,
And the refrigerant flows through a different number of bypass holes as the slide valve is rotated. 11. The method of claim 10,
Wherein the slide valve is provided so as to be in contact with one side of the compression bypass plate,
Wherein an area of contact between the slide valve and the compression bypass plate changes as the slide valve rotates. 11. The method of claim 10,
Wherein the compression bypass plate has a triangular cross section and is formed to extend in the axial direction so as to correspond to the first accommodating portion, the second accommodating portion, and the third accommodating portion. A chiller system comprising any one of the screw compressors of claims 1 to 14.

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