WO2014154046A1

WO2014154046A1 - Compressor system and control method therefor

Info

Publication number: WO2014154046A1
Application number: PCT/CN2014/070991
Authority: WO
Inventors: 肖传晶; 江超
Original assignee: 艾默生环境优化技术(苏州)有限公司
Priority date: 2013-03-29
Filing date: 2014-01-21
Publication date: 2014-10-02

Abstract

A compressor system (10A) comprises a first compressor (100) and a second compressor (200) connected in parallel to each other, a lubricant balance pipeline (500) disposed between the first compressor and the second compressor, a lubricant separator (A) connected to an air exhaust pipeline (40) and providing lubricant to the first compressor, and a first control valve (B) disposed inside the lubricant balance pipeline. The lubricant balance pipeline can be selectively opened or closed by using the first control valve (B). A control method for the compressor system. By means of the compressor system and the control method therefor, the lubricant balance between two or more compressors can be improved, and the lost is relatively low.

Description

Compressor system and control method thereof

This application is required to be submitted to the China Patent Office on March 29, 2013, with the application number 201310108052.6, the invention titled "Compressor System and Control Method", and submitted to the China Patent Office on March 29, 2013. The application number is 201320153166.8, the entire disclosure of which is hereby incorporated by reference in its entirety in its entirety in its entirety in the the the the the the the the the the Technical field

The invention relates to a compressor system and a control method therefor. Background technique

The content of this section merely provides background information related to the present disclosure, which may not constitute prior art. A compressor system consisting of two or more compressors in parallel is known. This compressor system can replace a single compressor with a large cooling capacity with a relatively small number of compressors, thereby reducing the cost of the system and improving the operating efficiency of the system. In such a compressor system in which a plurality of compressors are connected in parallel, an important problem is to ensure a lubricant balance between the respective compressors. Although various methods have been proposed to improve the lubricant balance in such compressor systems, there is still an improvement in lubricant balance in such compressor systems, particularly when including variable capacity compressors in compressor systems. Space. Therefore, there is a need for a compressor system in which the balance of lubricant between compressors is further improved. Summary of the invention

According to an aspect of the invention, a compressor system is provided, comprising: a first compressor, the first compressor including a first housing and a first air inlet disposed on the first housing and a first exhaust port, the second compressor, the second compressor includes a second housing, and second and second exhaust ports disposed on the second housing, the first inlet The air port and the second air inlet are in fluid communication with each other via an intake duct and are supplied via an intake duct a fluid, the first exhaust port and the second exhaust port being in fluid communication with each other via an exhaust duct and discharging a fluid via an exhaust duct; a lubricant separator, the lubricant separator being connected to the exhaust duct Separating the lubricant in the fluid flowing through the exhaust conduit, and the lubricant separator supplies the separated lubricant to the first compressor via a lubricant supply conduit; a lubricant balancing conduit, the lubrication a reagent balancing conduit disposed between the first compressor and the second compressor to enable lubricant within the first compressor to flow into the second compressor via the lubricant balancing conduit; And a first control valve, the first control valve being disposed in a section of the lubricant balancing conduit that is coupled to the first compressor and capable of being selectively opened or closed. According to another aspect of the present invention, there is provided a control method of a compressor system including a first compressor and a second compressor connected in parallel with each other, disposed in the first compressor, and the first a lubricant balance pipe between the two compressors, a common exhaust pipe disposed in the first compressor and the second compressor, and a lubricant supplied to the first compressor via a lubricant supply pipe a lubricant separator and a first control valve disposed in a section of the lubricant balance pipe connected to the first compressor, the control method characterized by: lubrication in the first compressor Opening the first control valve when the dose is greater than or equal to the first predetermined value, and closing the first control valve when the amount of lubricant in the first compressor is less than or equal to a second predetermined value, the first predetermined value being greater than The second predetermined value. DRAWINGS

Features and advantages of one or more embodiments of the present invention will become more apparent from the description of the accompanying drawings in which: Figure 1 is a schematic diagram of a conventional compressor system; Figure 3 is a schematic cross-sectional view of another compressor in the compressor system of Figure 1; Figure 4 is a compressor system in accordance with an embodiment of the present invention; Figure 5 is a schematic piping layout of a compressor system in accordance with an embodiment of the present invention; and Figure 6 is a schematic illustration of another fixed scroll component having a capacity adjustment function. detailed description

The following description of the preferred embodiments is merely exemplary and is in no way limiting of the invention The same reference numerals are used to denote the same parts in the respective drawings, and thus the description of the same components will not be repeated.

The basic construction and principle of a conventional compressor system will first be described with reference to Figs. As shown in FIG. 1, the compressor system 10 includes a first compressor 100, a second compressor 200, and a third compressor 300. The first compressor 100, the second compressor 200, and the third compressor 300 are connected in parallel to each other to constitute The so-called multi-line system. More specifically, the first compressor 100 may include a first housing 110 and a first intake port 118 and a first exhaust port 119 disposed on the first housing 110. The first housing 110 may include a first suction pressure zone and a first exhaust pressure zone (described later in detail with reference to FIG. 2) and a lubricant is stored in the first housing 110. In the construction of such a vertical compressor, the lubricant is typically stored in the bottom region of the first housing 110. Similarly, the second compressor 200 includes a second housing 210 and a second intake port 218 and a second exhaust port 219 disposed on the second housing 210. The second housing 210 may include a second suction pressure zone and a second exhaust pressure zone (described later in detail with reference to FIG. 3) and a lubricant is stored in the second housing 210. The third compressor 300 may have the same configuration as the second compressor 200. Specifically, the third compressor 300 may include a third housing 310 and a third intake port 318 and a third exhaust port 319 disposed on the third housing 310. The first intake port 118 , the second intake port 218 , and the third intake port 318 are in fluid communication with each other via the intake duct 410 and are supplied with fluid via the intake duct 410 . The first exhaust port 119 , the second exhaust port 219 , and the third exhaust port 319 are in fluid communication with each other via the exhaust duct 420 and discharge the fluid via the exhaust duct 420 . More specifically, the intake duct 410 may include a first intake manifold 412 connected to the first intake port 118, a second intake manifold 414 connected to the second intake port 218, and a third intake port 318. The third intake manifold 416 and the intake manifold 418 that connect the first intake manifold 412, the second intake manifold 414, and the third intake manifold 416 together. The intake air (suction fluid) in the compressor system 10 may be drawn in via the intake manifold 418, and then drawn into the first compressor 100 via the first intake manifold 412, the second intake manifold 414, and the third intake manifold 416, respectively. The second compressor 200 and the third compressor 300. Similarly, the exhaust duct 420 may include a first exhaust pipe 422 connected to the first exhaust port 119, a second exhaust pipe 424 connected to the second exhaust port 219, and a third exhaust port 319. a third exhaust manifold 426 and a first exhaust manifold 422, a second exhaust manifold 424, and a third exhaust manifold 426 Exhaust manifold 428 that is connected together. The compressed fluid in the first compressor 100, the second compressor 200, and the third compressor 300 is discharged through the first exhaust manifold 422, the second exhaust manifold 424, and the third exhaust manifold 426, respectively, and is exhausted. The manifolds 428 merge to be discharged together into the compressor system 10. A lubricant balance pipe 500 is provided between the first compressor 100, the second compressor 200, and the third compressor 300 to supply lubricant to each compressor and/or to enable lubricant in each compressor to pass via The lubricant balance pipes 330 flow to each other. For example, the lubricant balance pipe 500 may be respectively coupled to the lubricant balance port 117 provided in the first compressor 100, the lubricant balance port 217 provided in the second compressor 200, and the lubrication provided in the third compressor 300. The agent balance port 317 is connected. Additionally, section 510 of lubricant balancing conduit 500 may also be in fluid communication with a lubricant separator A (e.g., as shown in Figure 5) in compressor system 10 to supply lubricant to each compressor. Sensors 531, 532, and 533 for detecting the amount of lubricant in each compressor are respectively disposed on the first compressor 100, the second compressor 200, and the third compressor 300. Control valves 541, 542, and 543 are provided in the vicinity of the lubricant balance ports 117, 217, and 317, respectively. Control components of the compressor system (for example, a control circuit board or an electronic control unit (ECU), etc.) can individually control the opening or closing of the respective control valves 541, 542, and 543 according to the measurement results of the respective sensors 531, 532, and 533, thereby Adjust the amount of lubricant in each compressor. 2 and 3, the specific configuration of the compressor system 10 will be more specifically described by taking a variable capacity scroll compressor and a fixed capacity scroll compressor as an example. Figure 2 shows an example of a conventional fixed capacity scroll compressor. The second compressor 200 or the third compressor 300 in FIG. 1 may employ a compressor of the configuration shown in FIG. 2, but is not limited thereto. The configuration of the compressor 200 will be specifically described below taking the second compressor 200 as an example. The housing 210 (the second housing 210 described above) of the scroll compressor 200 shown in FIG. 2 includes a substantially cylindrical body 211, a top cover 212 disposed at one end of the body 211, and a bottom cover disposed at the other end of the body 211. 214. A partition 216 is disposed between the top cover 212 and the body 211 to partition the internal space of the compressor into a high pressure side (ie, a discharge pressure zone) and a low pressure side (ie, an intake pressure zone). A high pressure side is formed between the partition 216 and the top cover 212, and a low pressure side is formed between the partition 216, the body 211 and the bottom cover 214. An intake port 218 for taking in a fluid is provided on the low pressure side, and an exhaust port 219 for discharging the compressed fluid is provided on the high pressure side. Although the vent 219 is shown in the top center of the top cover 212 in FIG. 2, it will be understood by those skilled in the art that the vent 219 can also be disposed on the side of the top cover 212 as shown in FIG. Shell A motor 220 composed of a stator 222 and a rotor 224 is disposed in the body 210. A drive shaft 230 is disposed in the rotor 224 to drive a compression mechanism composed of the fixed scroll member 250 and the orbiting scroll member 260. The movable scroll member 260 includes an end plate 264, a hub portion 262 formed on one side of the end plate, and a spiral blade 266 formed on the other side of the end plate. The fixed scroll member 250 includes an end plate 254, a spiral blade 256 formed on one side of the end plate, and a vent hole 252 formed at a substantially central position of the end plate. A series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side are formed between the scroll vanes 256 of the fixed scroll member 250 and the scroll vanes 266 of the orbiting scroll member 260. Wherein, the radially outermost compression chamber is at the suction pressure, and the radially innermost compression chamber is at the exhaust pressure. The intermediate compression chamber is between the suction pressure and the discharge pressure and is therefore also referred to as the medium pressure chamber. One side of the movable scroll member 260 is supported by an upper portion of the main bearing housing 240 (which constitutes a thrust member), and one end of the drive shaft 230 is supported by a main bearing 244 provided in the main bearing housing 240. One end of the drive shaft 230 is provided with an eccentric crank pin 232, and an unloading bushing 242 is provided between the eccentric crank pin 232 and the hub portion 262 of the orbiting scroll member 260. By the driving of the motor 220, the orbiting scroll member 260 will rotate normally with respect to the fixed scroll member 250 (i.e., the central axis of the orbiting scroll member 260 is rotated about the central axis of the scroll member 250, but the orbiting scroll member 260 is rotated. It does not rotate itself about its central axis) to achieve fluid compression. The translational rotation described above is achieved by a cross slip ring disposed between the fixed scroll member 250 and the movable scroll member 260. In order to prevent the high pressure side fluid from flowing back to the low pressure side via the air hole 252 under certain conditions, a check valve or exhaust valve 270 may be provided at the exhaust hole 252. In order to achieve fluid compression, the fixed scroll member 250 and the orbiting scroll member 260 must be effectively sealed. In one aspect, the distal end portion of the scroll blade 256 of the fixed scroll member 250 and the end plate 264 of the orbiting scroll member 260 and the distal end portion of the scroll blade 266 of the orbiting scroll member 260 and the fixed scroll member 250 An axial seal is required between the end plates 254. Typically, a back pressure chamber 258 is provided on the opposite side of the end plate 254 of the fixed scroll member 250 from the scroll vanes 256. A seal assembly 280 is disposed in the back pressure chamber 258, and the axial displacement of the seal assembly 280 is limited by the diaphragm 216. The back pressure chamber 258 is in fluid communication with the intermediate pressure chamber through an axially extending through bore (not shown) formed in the end plate 254 to form a force that urges the fixed scroll member 250 toward the orbiting scroll member 260. Since one side of the orbiting scroll member 260 is supported by the upper portion of the main bearing housing 240, the fixed scroll member 250 and the orbiting scroll member 260 can be effectively pressed together by the pressure in the back pressure chamber 258. When the pressure in each compression chamber exceeds the set value, The fixed scroll member 250 is moved upward. At this time, the fluid in the compression chamber will pass through the gap between the distal end portion of the scroll vane 256 of the fixed scroll member 250 and the end plate 264 of the orbiting scroll member 260 and the scroll vane 266 of the orbiting scroll member 260. The gap between the distal end portion and the end plate 254 of the fixed scroll member 250 leaks to the low pressure side to effect unloading, thereby providing axial flexibility to the scroll compressor. On the other hand, a radial seal is also required between the side surface of the scroll blade 256 of the fixed scroll member 250 and the side surface of the scroll blade 266 of the orbiting scroll member 260. This radial sealing between the two is typically achieved by the centrifugal force of the orbiting scroll member 260 during operation and the driving force provided by the drive shaft 230. Specifically, during operation, by the driving of the motor 220, the orbiting scroll member 260 will rotate in translation with respect to the fixed scroll member 250, so that the orbiting scroll member 260 will generate centrifugal force. On the other hand, the eccentric crank pin 232 of the drive shaft 230 also generates a driving force component that contributes to the radial sealing of the fixed scroll member and the movable scroll member during the rotation. The scroll vanes 266 of the orbiting scroll member 260 abut against the scroll vanes 256 of the fixed scroll member 250 by means of the centrifugal force and driving force components described above, thereby achieving a radial seal therebetween. When incompressible materials (such as solid impurities, lubricating oil, and liquid refrigerant) enter the compression chamber and get caught between the swirl vanes 256 and the swirl vanes 266, the scroll vanes 256 and the swirl vanes 266 can be temporarily radially They are separated from each other to allow foreign matter to pass, thus preventing the vortex blades 256 or 266 from being damaged. This ability to be radially separated provides radial flexibility to the scroll compressor, increasing compressor reliability. During operation of the compressor 200, lubricant stored at the bottom of the housing 210 may be supplied to the end of the eccentric crank pin 232 via the oil supply passage 233 formed in the drive shaft 230 and under the action of gravity and centrifugal force Flow and splash to lubricate and cool other moving parts in the compressor. Figure 3 shows a conventional variable capacity scroll compressor. The first compressor 100 in Fig. 1 can adopt the configuration of the compressor shown in Fig. 3, but is not limited thereto. The basic structure of the scroll compressor 100 shown in Fig. 3 is substantially the same as that of the scroll compressor 200 shown in Fig. 2 . Briefly, the housing 110 of the scroll compressor 100 (the first housing 110 described above) includes a substantially cylindrical body 111, a top cover 112, and a bottom cover 114. A partition 116 is disposed between the top cover 112 and the body 111 to partition the internal space of the compressor into a high pressure side (ie, a discharge pressure zone) and a low pressure side (ie, an intake pressure zone). A high pressure side is formed between the partition 116 and the top cover 112, and a low pressure side is formed between the partition 116, the body 111 and the bottom cover 114. Useful on the low pressure side In the intake port 118 for sucking fluid (see FIG. 1, not shown in FIG. 3), an exhaust port 119 for discharging the compressed fluid is disposed on the high pressure side (see FIG. 1, not shown in FIG. ). A motor 120 composed of a stator 122 and a rotor 124 is disposed in the housing 110. A drive shaft 130 is provided in the rotor 124 to drive a compression mechanism composed of the fixed scroll member 150 and the movable scroll member 160. The movable scroll member 160 includes an end plate 164, a hub portion 162 formed on one side of the end plate, and a spiral blade 166 formed on the other side of the end plate. The fixed scroll member 150 includes an end plate 154, a spiral blade 156 formed on one side of the end plate, and a vent hole 152 formed at a substantially central position of the end plate. One side of the movable scroll member 160 is supported by an upper portion of the main bearing housing 140 (which constitutes a thrust member), and one end of the drive shaft 130 is supported by a main bearing 144 provided in the main bearing housing 140. One end of the drive shaft 130 is provided with an eccentric crank pin 132, and an unloading bushing 142 is disposed between the eccentric crank pin 132 and the hub portion 162 of the movable scroll member 160. A back pressure chamber 158 is disposed on a side of the end plate 154 of the fixed scroll member 150 opposite to the scroll vane 156. A seal assembly 180 is disposed in the back pressure chamber 158, and the axial displacement of the seal assembly 180 is limited by the diaphragm 116. During operation of the compressor 100, lubricant stored at the bottom of the housing 110 may be supplied to the end of the eccentric crank pin 132 via the oil supply passage 133 formed in the drive shaft 130 and under the action of gravity and centrifugal force Flow and splash to lubricate and cool other moving parts in the compressor. The variable capacity scroll compressor 100 shown in FIG. 3 further includes a capacity adjustment mechanism 190 configured such that the fixed scroll member 150 and the orbiting scroll member 160 are separated or engaged with each other in the axial direction of the compressor 100. More specifically, the capacity adjustment mechanism 190 may include a piston 192 coupled to the fixed scroll member 150 and a cylinder 194 fixed relative to the housing 110. The piston 192 is slidable within the cylinder 194 to drive the fixed scroll member 150 to move in the axial direction. The space S between the top surface of the piston 192 and the cylinder 194 may be in fluid communication with the exhaust pressure zone of the compressor 100 via a passage 193 (or a passage formed in the cylinder 194) in the piston 192. Additionally, the space S between the top surface of the piston 192 and the cylinder 194 may also be in fluid communication with the suction pressure zone or intake conduit 410 of the compressor 100 via the joint 195. A capacity adjustment control valve may be provided in the conduit between the joint 195 and the suction pressure zone or intake conduit 410 to control fluid communication between the space S and the suction pressure zone. The compressor 100 can achieve capacity adjustment of the compressor by alternately performing a loading operation and an unloading operation. For example, when performing a loading operation, the capacity adjustment control valve is closed to block fluid communication between the space S and the suction pressure zone. At this time, the pressure in the space S is the same as the pressure in the exhaust pressure region, and therefore, the fixed scroll member 150 is engaged with the orbiting scroll member 160 under the pressure in the back pressure chamber 158 to effect fluid compression. Capacity adjustment when implementing the uninstall operation The throttle control valve opens to allow fluid communication between the space S and the suction pressure zone. At this time, space

The fluid in S flows to the exhaust pressure zone such that the pressure in space S is less than the pressure in the exhaust pressure zone. Therefore, the piston 192 moves upward by the pressure difference and drives the fixed scroll member 150 to move upward to be separated from the orbiting scroll member 160 in the axial direction. At this time, the compression mechanism constituted by the movable scroll member 160 and the fixed scroll member 150 is not fluid-compressed. When the recovery loading operation is required, the capacity adjustment control valve is closed, and since the space S is in fluid communication with the exhaust pressure region via the passage 193, the pressure in the space S gradually becomes equal to the pressure in the exhaust pressure region. Thus, the fixed scroll member 150 is again engaged with the orbiting scroll member 160 by the pressure in the back pressure chamber 158. The compressor 100 is capable of achieving capacity adjustment from 0% to 100% by controlling the loading operation and the unloading operation of the capacity adjustment mechanism 190, for example, in a duty ratio manner. The capacity adjustment mechanism shown in Fig. 3 is described in detail in the applicant's published patent document CN100460683C, the entire contents of which is incorporated herein by reference. In the case of employing the compressor system 10 consisting of the compressors 100, 200 and 300 as above, for example, when the compressors 100, 200 and 300 have the same capacity (both 100%), the entire compressor system 10 can be supplied from 0. % to 300% capacity adjustment. For example, when the first compressor 100 is operated and the second compressor 200 and the third compressor 300 are stopped, the compressor system 10 can achieve a capacity adjustment of 0% to 100%; when the first compressor 100 and the second compressor When both are operating and the third compressor 300 is stopped, the compressor system 10 can achieve a capacity adjustment of 100% to 200%; when the first compressor 100, the second compressor 200, and the third compressor 300 are both operated, compression The machine system 10 can achieve a capacity adjustment of 200% to 300%. It will be understood by those skilled in the art that a further fixed capacity or variable capacity compressor may be connected in parallel in the compressor system 10, or may be composed only of the first compressor 100 and the second compressor 200. Thus, the compressor system constructed as above can achieve more flexible capacity modulation, greater total capacity, and lower cost. However, in such a compressor system 10, it is necessary to adjust and balance the respective compressors using three sensors 531, 532, 533 and three control valves 541, 542, 543 corresponding to the number of compressors in the compressor system. The amount of lubricant between them, so the cost of the entire compressor system is relatively high. In addition, the control logic between the various control valves 541, 542, 543 is also complicated. Next, a compressor system 10A according to an embodiment of the present invention will be described with reference to Figs. The basic configuration of the compressor system 10A is larger than the basic configuration of the compressor system 10 shown in FIG. The same reference numerals are used to refer to the same components in FIG. 4 and a detailed description of these components will be omitted. In the compressor system 10A according to an embodiment of the present invention, three compressors connected in parallel with each other, that is, the first compressor 100, the second compressor 200, and the third compressor 300 are included to constitute a so-called multi-compressor Online system. It will be understood by those skilled in the art that the compressor system 10A according to the present invention may also include only two parallel compressors, namely the first compressor 100 and the second compressor 200, or may include more parallel compressors. The intake ports of the respective compressors may be in fluid communication with each other via a common intake conduit 410 and supplied with fluid, and the exhaust ports of the respective compressors may be in fluid communication with each other and exhaust fluid via a common exhaust conduit 420. The compressor system 10A further includes a lubricant separator A coupled to the common exhaust conduit 420 to separate the lubricant in the fluid flowing through the exhaust conduit 420. Each of the compressors 100, 200, and 300 communicates with each other via a common lubricant balancing conduit 500 to allow lubricant within the first compressor 100 to flow to the second compressor 200 and/or via the lubricant balancing conduit 500. Within the three compressors 300. In the compressor system 10A according to the present invention, the lubricant separator A supplies the separated lubricant to the first compressor 100 only via the lubricant supply pipe 700. In particular, in the compressor system 10A according to the present invention, the sensor H for detecting the amount of lubricant may be provided only on the first compressor 100 (for example, corresponding to the sensor 531 shown in Fig. 1), and may be omitted. Sensors for detecting the amount of lubricant on the second compressor 200 and the third compressor 300. Here, the sensor H may be a liquid level sensor, but is not limited thereto. In addition, in the compressor system 10A, the first control valve B (for example, corresponding to the control valve 541 shown in FIG. 1) may be provided only in the section of the lubricant balance pipe 500 that is connected to the first compressor 100. To selectively open or close the lubricant balancing conduit 500. Further, a second control valve J may be provided in the lubricant supply conduit 700 to selectively supply lubricant from the lubricant separator A to the first compressor 100. The first control valve B and the second control valve J may be solenoid valves, but are not limited thereto. The first control valve B and/or the second control valve J may be controlled by a control component 800 (see FIG. 5) such as a control circuit board or an electronic control unit (ECU) in the compressor system 10A to achieve a desired lubricant balance. . In other words, the control unit 800 can control the opening, closing, or opening of the first control valve B and/or the second control valve J based on the measurement data of the sensor H. More specifically, the total amount of lubricant is constant throughout the compressor system 10A. The lubricant contained in the exhaust of each of the compressors 100, 200, and 300 is subjected to the lubricant separator. A is separated and stored in the lubricant separator A. Since the lubricant separator in the lubricant separator A is the suction pressure and the lubricant storage region in the casing of the compressor 100 is the suction pressure, the lubricant in the lubricant separator A can flow to the first under the action of the pressure difference. In the compressor 100. The first control valve B may be opened when the amount of lubricant in the first compressor 100 reaches a certain value, so that the lubricant in the first compressor 100 can flow to other compressors via the lubricant balance pipe 500 under the action of gravity. 200 and / or 300 to replenish lubricants to other compressors. More specifically, the control part 800 may be configured to open the first control valve B when the measurement data of the sensor H is greater than or equal to the first predetermined value to allow the lubricant to be supplied to the other compressor, and the measurement data at the sensor H is less than or equal to the second The first control valve B is closed at a predetermined value to stop the supply of lubricant to other compressors. The first predetermined value may be set to be greater than the second predetermined value. In order to ensure the authenticity of the measurement data of the sensor H due to fluctuations in the lubricant or the like in the first compressor, the control unit may be further configured such that the measurement data at the sensor H is greater than or equal to a first predetermined value for a first predetermined time (eg The first control valve B is opened at 5 seconds), and the first control valve B is closed when the measured data of the sensor is less than or equal to the second predetermined value for a second predetermined time (for example, may also be 5 seconds). In addition, the control part 800 may be further configured to close the second control valve J to stop the supply of lubricant from the lubricant separator A to the first compressor 100 when the measured data of the sensor H is greater than or equal to the third predetermined value, and at the sensor When the measured data of H is less than or equal to the fourth predetermined value, the second control valve J is opened to start the supply of lubricant from the lubricant separator A to the first compressor 100. The third predetermined value may be greater than or equal to a first predetermined value, and the fourth predetermined value may be less than or equal to a second predetermined value. Similarly, in order to ensure the authenticity of the measurement data of the sensor H, the control part 800 may be configured to close the second control valve J when the measurement data of the sensor H is greater than or equal to a third predetermined value and last for a third predetermined time, and at the sensor H The second control valve J is opened when the measurement data is less than or equal to the fourth predetermined value and continues for the fourth predetermined time. Each of the above parameters: the first predetermined value, the second predetermined value, the third predetermined value, the fourth predetermined value, the first predetermined time, the second predetermined time, the third predetermined time, and the fourth predetermined time are further according to the compressor 100 and The specific characteristics of the compressor system 10A, the operating conditions, and the like are set in advance. More simply, the control component 800 can be configured to control the second control valve J in logic opposite the first control valve B. That is, the control part 800 can be configured to close when the first control valve B is opened The second control valve J is closed, and the second control valve J is opened when the first control valve B is closed. Thereby, the control logic of each control valve can be further simplified. On the other hand, when the first compressor 100 is a variable capacity compressor as shown in FIG. 3, since the compression mechanism in the compressor does not generate a fluid pumping action (causing a pressure drop) when the compressor is in an unloaded state. Therefore, even if the suction pressures of the respective compressors are the same, the pressure in the suction pressure region of the variable capacity compressor is actually slightly lower than the pressure in the suction pressure region of the fixed capacity compressor. In this case, when the control valve B is opened, the lubricant in the first compressor 100 can flow into the other compressors 200 and 300 under the action of both gravity and differential pressure. Further, when the first compressor 100 is a fixed capacity compressor as shown in FIG. 2, the first section of the intake duct 410 connected to the first compressor 100 may be configured to provide a ratio of the intake duct 410 The second section of the second compressor 200 (and/or the third compressor 300) is connected to a smaller fluid resistance. For example, the fluid resistance of the first section may be made smaller than the fluid of the second section by selecting at least one of the length of the first section and the second section, the cross-sectional area, the angle of the bend, and the number of bends. resistance. In this case, in the case where the suction pressure of the compressor system 10A is the same, since the fluid resistance of the first section supplying the fluid to the first compressor 100 is small, the suction pressure in the first compressor 100 is The pressure in the zone will actually be slightly higher than the pressure in the suction pressure zone in the other compressors. Therefore, when the first control valve B is opened, the lubricant in the first compressor 100 can be supplied from the first compressor 100 to the other not only under the action of gravity but also under the influence of the suction pressure difference of each compressor. Compressors 200, 300. Thereby, the supply of lubricant to other compressors is further ensured. It will be understood by those skilled in the art that the above-described technical means for realizing the change of the fluid resistance by modifying the parameters of the first section and the second section can also be applied in combination to the case where the first compressor 100 is a variable capacity compressor. Or, more broadly, regardless of whether the first compressor 100 is a fixed capacity compressor or a variable capacity compressor, the first compressor 100 may be configured to have a lower suction pressure than the second compressor 200 in any manner. . Further, in order to make the lubricant more evenly distributed between the second compressor 200 and the third compressor 300, a gas balance pipe may be disposed between the second compressor 200 and the third compressor 300.

The compressor system 10A of the above configuration can have the following advantageous effects and modifications. The first compressor 100 may be a variable capacity compressor or a fixed capacity compressor. In both cases, since only one sensor and one control can be used in the compressor system Valve B is used to achieve lubricant supply and/or balance between the various compressors, thus reducing the cost of the overall system and simplifying the control logic of the system. Further, in the case where the first compressor 100 is a variable capacity compressor, since the lubricant in the lubricant separator A is first supplied to the first compressor 100, the first compressor having a relatively high cost is preferentially secured. The lubricant supply of 100 reduces the likelihood of failure or damage to the first compressor 100. In the case where the first compressor 100 is a variable capacity compressor, the first compressor 100 may employ the one shown in FIG. 3 such that the fixed scroll member 150 and the orbiting scroll member 160 are separated or joined to each other in the axial direction. Variable capacity mechanism 190. However, the first compressor 100 can also use other types of variable capacity compressors. For example, the first compressor 100 may be an inverter compressor in which the adjustment of the capacity can be achieved by changing the rotational speed of the motor. For another example, referring to FIG. 6, at least one pressure relief passage 153 that provides fluid communication between the suction pressure zone and one of the compression chambers may be formed in the fixed scroll member 150A of the first compressor 100, which may be in the pressure relief passage 153. A control valve 155 that can be selectively opened is provided. When the control valve 155 is closed, all of the compression chambers are subjected to a compression operation, and when the control valve 155 is opened, a portion of the compression chamber is depressurized so that the compressor is allowed to have a partial capacity. The capacity adjustment configuration shown in Fig. 6 is described in detail in the applicant's already disclosed Chinese utility model patent CN2027487U, and will not be further described herein. The entire content of this document CN2027487U is incorporated herein by reference.

Additionally, in the above embodiment, compressor system 10A includes three compressors, but those skilled in the art will appreciate that compressor system 10A may include two or more than three compressors to achieve less or more total capacity.

Further, in the above embodiment, the control valve J is employed to control the opening and closing of the lubricant supply pipe 700. However, in other embodiments, a throttling element such as a capillary tube may be used in place of the control valve 1. In this case, the lubricant in the lubricant separator A is always supplied to the first compressor 100 via the throttle element. The optimum aperture of the throttling element can be selected in advance by experiment or the like. Control valve B can still be controlled to open or close by the above control logic. In this way, the cost of the compressor system can be further reduced and the control logic can be simplified.

Further, in the above embodiment, the first compressor 100, the second compressor 200, and the third compressor 300 are shown as scroll compressors, but those skilled in the art will understand that these compressors may be selected from piston compression, respectively. A group consisting of a machine, a rotor compressor, a screw compressor, and a centrifugal compressor. Additionally, the first compressor and the second compressor (or third compressor) may be the same type of compressor or different types of compressors to achieve a more flexible system arrangement. The embodiments and various modifications of the present invention have been described above, and the basic concepts of the present invention are summarized as follows:

According to a first aspect of the present invention, a compressor system is provided, comprising: a first compressor, the first compressor including a first housing and a first air inlet disposed on the first housing And a first exhaust port; the second compressor, the second compressor includes a second housing and second and second exhaust ports disposed on the second housing, the first The intake port and the second intake port are in fluid communication with each other via an intake duct and are supplied with fluid via an intake duct, the first exhaust port and the second exhaust port being in fluid communication with each other via an exhaust duct And discharging the fluid via an exhaust conduit; a lubricant separator connected to the exhaust conduit to separate lubricant in the fluid flowing through the exhaust conduit, and the lubricant separator via the lubricant a supply pipe selectively supplies the separated lubricant to the first compressor; a lubricant balance pipe disposed between the first compressor and the second compressor Making the first compressor An internal lubricant can flow into the second compressor via the lubricant balancing conduit; and a first control valve disposed in the lubricant balancing conduit and the first compressor In the connected section and can be selectively opened or closed.

According to a second aspect of the invention, a sensor for detecting the amount of lubricant in the first compressor is provided in the first compressor.

According to a third aspect of the invention, the sensor is a level sensor.

According to a fourth aspect of the invention, the compressor system further includes a control unit configured to control opening or closing of the first control valve based on measurement data of the sensor.

According to a fifth aspect of the invention, the control unit is configured to open the first control valve when the measurement data of the sensor is greater than or equal to a first predetermined value, and the measurement data at the sensor is less than or equal to a second predetermined value The first control valve is closed when the first predetermined value is greater than the second predetermined value.

According to a sixth aspect of the invention, the control unit is further configured to open the first control valve when the measurement data of the sensor is greater than or equal to the first predetermined value for a first predetermined time, and at the sensor The first control valve is closed when the measured data is less than or equal to the second predetermined value and continues for a second predetermined time.

According to a seventh aspect of the invention, a second control valve is provided in the lubricant supply conduit. According to an eighth aspect of the invention, the control component is further configured to be at the sensor The second control valve is closed when the measured data is greater than or equal to a third predetermined value, and the second control valve is opened when the measured data of the sensor is less than or equal to a fourth predetermined value.

According to a ninth aspect of the invention, the third predetermined value is greater than or equal to the first predetermined value, and the fourth predetermined value is less than or equal to the second predetermined value.

According to a tenth aspect of the invention, the control unit is further configured to close the second control valve when the measurement data of the sensor is greater than or equal to the third predetermined value for a third predetermined time, and at the sensor The second control valve is opened when the measured data is less than or equal to the fourth predetermined value and continues for a fourth predetermined time.

According to an eleventh aspect of the present invention, the control unit is further configured to control the second control valve in a reverse phase opposite to the first control valve.

According to a twelfth aspect of the invention, the first compressor is a variable capacity compressor.

According to a thirteenth aspect of the invention, the first compressor includes an orbiting scroll member, a fixed scroll member, and a capacity adjustment mechanism, and the capacity adjustment mechanism is configured such that the fixed scroll member and the movable scroll The components are separated or joined to each other in the axial direction.

According to a fourteenth aspect of the invention, the first compressor is an inverter compressor.

According to a fifteenth aspect of the invention, the first compressor includes an orbiting scroll member and a fixed scroll member, and the movable scroll member and the fixed scroll member form a series of volumes from the radially outer side toward a compression chamber having a radially inner side gradually decreasing, wherein at least one pressure relief passage is provided in the fixed scroll member to provide fluid communication between the suction pressure region and one of the compression chambers, wherein the pressure relief passage is A third control valve that can be selectively opened is provided.

According to a sixteenth aspect of the invention, the first compressor is a fixed capacity compressor.

According to a seventeenth aspect of the invention, the second compressor is a fixed capacity compressor.

According to an eighteenth aspect of the invention, the first compressor and the second compressor are both scroll compressors.

According to a nineteenth aspect of the invention, the first compressor and the second compressor are respectively selected from the group consisting of a piston compressor, a rotor compressor, a screw compressor, and a centrifugal compressor.

According to a twentieth aspect of the invention, the first compressor and the second compressor are the same type of compressor.

According to a twenty first aspect of the invention, the first compressor and the second compressor are different types of compressors. According to a twenty-second aspect of the invention, the first section of the intake duct connected to the first compressor is configured to provide a second connection with the second compressor than the intake duct Smaller fluid resistance in the section.

According to a twenty-third aspect of the invention, the first part is made by selecting at least one of a length, a cross-sectional area, an angle of bending, and a number of bending of the first section and the second section The fluid resistance of a section is less than the fluid resistance of the second section.

According to a twenty-fourth aspect of the invention, the compressor system further includes a third compressor, the third intake port of the third compressor being respectively connected to the first compressor via the intake duct An air inlet is in fluid communication with a second air inlet of the second compressor, and a third air outlet of the third compressor is respectively connected to the first row of the first compressor via the exhaust duct A port is in fluid communication with a second exhaust port of the second compressor, and the third compressor is in fluid communication with the first compressor and the second compressor via the lubricant balancing conduit.

According to a twenty-fifth aspect of the invention, a gas balance pipe is disposed between the second compressor and the third compressor.

According to a twenty-sixth aspect of the invention, a throttle element is provided in the lubricant supply pipe.

According to a twenty-seventh aspect of the invention, the throttling element is a capillary tube.

According to a twenty-eighth aspect of the invention, the first compression mechanism is caused to have a lower suction pressure than the second compressor.

According to a twenty-ninth aspect of the present invention, a control method of a compressor system including a first compressor and a second compressor connected in parallel with each other, and a first compressor and a a lubricant balance pipe between the second compressors, disposed in a common exhaust pipe of the first compressor and the second compressor, and supplying lubrication to the first compressor via a lubricant supply pipe a lubricant separator of the agent and a first control valve disposed in a section of the lubricant balance pipe connected to the first compressor, the control method characterized by: in the first compressor The first control valve is opened when the amount of lubricant is greater than or equal to a first predetermined value, and the first control valve is closed when the amount of lubricant in the first compressor is less than or equal to a second predetermined value, the first predetermined The value is greater than the second predetermined value.

According to a thirtieth aspect of the invention, the compressor system further includes a second control valve disposed in the lubricant supply conduit.

According to a thirty-first aspect of the invention, the second control valve is closed when the amount of lubricant in the first compressor is greater than or equal to a third predetermined value, and the lubricant in the first compressor The second control valve is opened when the amount is less than or equal to a fourth predetermined value.

According to a thirty-second aspect of the invention, the third predetermined value is greater than or equal to the first predetermined value, and the fourth predetermined value is less than or equal to the second predetermined value.

According to a thirty-third aspect of the invention, the second control valve is controlled in logic opposite to the first control valve.

Although the various embodiments of the present invention have been described in detail herein, it is understood that the invention is not limited to The skilled person implements other variations and variants. All such variations and modifications are intended to fall within the scope of the invention. Moreover, all of the components described herein can be replaced by other technically equivalent components.

Claims

1. A compressor system (10A) comprising:

a first compressor (100), the first compressor (100) including a first housing (110) and a first air inlet (118) and a first one disposed on the first housing (110) An exhaust port (119); a second compressor (200), the second compressor (200) including a second housing (210) and a second intake air disposed on the second housing (210) a port (218) and a second exhaust port (219), the first intake port (118) and the second intake port (218) being in fluid communication with each other via an intake duct (410) and via an intake duct (410) is supplied with a fluid, the first exhaust port (119) and the second exhaust port (219) being in fluid communication with each other via an exhaust duct (420) and discharging fluid via an exhaust duct (420);

a lubricant separator (A), the lubricant separator (A) is coupled to the exhaust conduit (420) to separate a lubricant in a fluid flowing through the exhaust conduit (420), and the lubricant is separated The (A) supplies the separated lubricant to the first compressor (100) via a lubricant supply conduit (700);

a lubricant balancing pipe (500), the lubricant balancing pipe (500) being disposed between the first compressor (100) and the second compressor (200) to make the first compressor (100) a lubricant can flow into the second compressor (200) via the lubricant balancing conduit (500);

a first control valve (B), the first control valve (B) being disposed in a section of the lubricant balancing conduit (500) connected to the first compressor (100) and capable of being selectively Turn it on or off.

The compressor system according to claim 1, wherein a sensor (H) for detecting the amount of lubricant in the first compressor (100) is provided in the first compressor (100).

3. The compressor system according to claim 2, wherein said sensor (H) is a liquid level sensor.

4. The compressor system of claim 2, further comprising a control component (800), The control unit is configured to control opening or closing of the first control valve (B) based on measurement data of the sensor (H).

5. The compressor system according to claim 4, wherein said control unit (800) is configured to open said first control valve (B) when said measured data of said sensor (H) is greater than or equal to a first predetermined value And closing the first control valve (B) when the measured data of the sensor (H) is less than or equal to a second predetermined value, the first predetermined value being greater than the second predetermined value.

6. The compressor system according to claim 5, wherein said control unit (800) is further configured to open when measurement data of said sensor (H) is greater than or equal to said first predetermined value for a first predetermined time The first control valve (B), and closing the first control valve (B) when the measured data of the sensor (H) is less than or equal to the second predetermined value for a second predetermined time.

The compressor system according to claim 5, wherein a second control valve (J) is disposed in said lubricant supply pipe (700).

8. The compressor system according to claim 7, wherein the control unit (800) is further configured to close the second control valve when the measured data of the sensor (H) is greater than or equal to a third predetermined value ( j), and opening the second control valve (J) when the measured data of the sensor (H) is less than or equal to a fourth predetermined value.

The compressor system according to claim 8, wherein said third predetermined value is greater than or equal to said first predetermined value, and said fourth predetermined value is less than or equal to said second predetermined value.

10. The compressor system according to claim 8, wherein the control part (800) is further configured to be configured when the measurement data of the sensor (H) is greater than or equal to the third predetermined value for a third predetermined time The second control valve (J) is closed, and the second control valve (j) is opened when the measured data of the sensor (H) is less than or equal to the fourth predetermined value and continues for a fourth predetermined time. 11. The compressor system of claim 7, wherein the control component (800) is further configured to control the second control valve (J) in logic opposite the first control valve (B).

The compressor system according to any one of claims 1 to 11, wherein the first compressor (100) is a variable capacity compressor.

13. The compressor system according to claim 12, wherein said first compressor (100) comprises an orbiting scroll member (160), a fixed scroll member (150), and a capacity adjustment mechanism (190), said capacity The adjustment mechanism (190) is configured such that the fixed scroll member (150) and the orbiting scroll member (160) are separated or joined to each other in the axial direction.

The compressor system according to any one of claims 1 to 11, wherein the first compressor (100) is an inverter compressor.

The compressor system according to any one of claims 1 to 11, wherein the first compressor (100) comprises an orbiting scroll member (160) and a fixed scroll member (150), the movable vortex Rotating part

(160) and the fixed scroll member (150) form a series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side, and at least one of the fixed scroll members (150) is formed A pressure relief passage (153) is provided in fluid communication between the suction pressure zone and one of the compression chambers, and a third control valve (155) capable of selectively opening is disposed in the pressure relief passage (153).

The compressor system according to any one of claims 1 to 11, wherein the first compressor (100) is a fixed capacity compressor.

The compressor system according to any one of claims 1 to 11, wherein the second compressor (200) is a fixed capacity compressor.

The compressor system according to any one of claims 1 to 11, wherein the first compressor (100) and the second compressor (200) are both scroll compressors. The compressor system according to any one of claims 1 to 11, wherein the first compressor (100) and the second compressor (200) are respectively selected from a piston compressor and a rotor compressor , a group consisting of a screw compressor and a centrifugal compressor.

The compressor system according to any one of claims 1 to 11, wherein the first compressor (100) and the second compressor (200) are the same type of compressor.

The compressor system according to any one of claims 1 to 11, wherein the first compressor (100) and the second compressor (200) are different types of compressors.

The compressor system according to any one of claims 1 to 11, wherein a first section of the intake duct (410) connected to the first compressor (100) is configured to provide a ratio The second section of the intake conduit (410) that is coupled to the second compressor (200) has a lower fluid resistance.

23. The compressor system of claim 22, wherein at least one of a length, a cross-sectional area, an angle of the bend, and a number of bends of the first and second sections is selected The fluid resistance of the first section is made less than the fluid resistance of the second section.

The compressor system according to any one of claims 1 to 11, further comprising a third compressor (300) via which the third intake port (318) of the third compressor (300) is An intake duct (410) is in fluid communication with a first intake port (118) of the first compressor (100) and a second intake port (218) of the second compressor (200), respectively a third exhaust port (319) of the third compressor (300) is respectively connected to the first exhaust port (119) and the second of the first compressor (100) via the exhaust duct (420) a second exhaust port (219) of the compressor (200) is in fluid communication, and the third compressor (300) is coupled to the first compressor (100) via the lubricant balancing conduit (500) The second compressor (200) is in fluid communication.

25. The compressor system of claim 24, wherein said second compressor (200) A gas balance conduit (600) is disposed between the third compressor (300).

26. The compressor system of claim 5, wherein a throttling element is disposed in the lubricant supply conduit (700).

27. The compressor system of claim 26, wherein the throttling element is a capillary

The compressor system according to any one of claims 1 to 11, wherein the first compressor (100) is configured to have a lower suction pressure than the second compressor (200).

29. A method of controlling a compressor system (10A), comprising: a first compressor (100) and a second compressor (200) connected in parallel with each other, disposed in the first compressor (100) and a lubricant balance pipe (500) between the second compressor (200), a common exhaust gas disposed in the first compressor (100) and the second compressor (200) a lubricant separator (A) that supplies lubricant to the first compressor (100) via a lubricant supply conduit (700) and a chamber disposed in the lubricant balance conduit (500) The first control valve (B) in the section to which the first compressor (100) is connected, the control method is characterized by:

Opening the first control valve (B) when the amount of lubricant in the first compressor (100) is greater than or equal to a first predetermined value, and the amount of lubricant in the first compressor (100) is less than or equal to The first control valve (B) is closed when the predetermined value is two, and the first predetermined value is greater than the second predetermined value.

The control method according to claim 29, wherein said compressor system (10A) further comprises a second control valve (J) disposed in said lubricant supply conduit (700).

The control method according to claim 30, wherein the second control valve (J) is closed when the amount of lubricant in the first compressor (100) is greater than or equal to a third predetermined value, and in the The second control valve (J) is opened when the amount of lubricant in a compressor (100) is less than or equal to a fourth predetermined value. The control method according to claim 31, wherein said third predetermined value is greater than or equal to said first predetermined value, and said fourth predetermined value is less than or equal to said second predetermined value.

The control method according to claim 30, wherein said second control valve (J) is controlled in logic opposite to said first control valve (B).