WO2021120656A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

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Publication number
WO2021120656A1
WO2021120656A1 PCT/CN2020/110165 CN2020110165W WO2021120656A1 WO 2021120656 A1 WO2021120656 A1 WO 2021120656A1 CN 2020110165 W CN2020110165 W CN 2020110165W WO 2021120656 A1 WO2021120656 A1 WO 2021120656A1
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WO
WIPO (PCT)
Prior art keywords
scroll
scroll compressor
pressure
port
compressor according
Prior art date
Application number
PCT/CN2020/110165
Other languages
English (en)
French (fr)
Inventor
王玉芳
杨春
束宏飞
Original Assignee
艾默生环境优化技术(苏州)有限公司
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Publication of WO2021120656A1 publication Critical patent/WO2021120656A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps

Definitions

  • the present disclosure relates to the technical field of scroll compressors, and more specifically, to a scroll compressor capable of adjusting capacity.
  • scroll compressors are compression machines of displacement compression.
  • the compression mechanism of a scroll compressor usually includes a fixed scroll component and a movable scroll component.
  • Capacity adjustment technology is an important direction in the development of refrigeration and heat pump systems, which can make the output capacity of the unit better adapt to the end load demand, reduce the start and stop of the unit, and improve the energy efficiency and comfort of the system.
  • Known compressors include various capacity adjustment mechanisms to change the operating capacity of the compressor.
  • the capacity adjustment mechanism can be used to operate the compressor under full load conditions or partial load conditions. The demand for full load changes or partial load changes depends on seasonal changes, occupants in the conditioned space, and/or refrigeration unit load requirements.
  • the capacity adjustment mechanism may include a fluid passage extending through the scroll member to selectively provide fluid communication between the compression chamber of the compressor and another pressure zone.
  • a fluid passage extending through the scroll member to selectively provide fluid communication between the compression chamber of the compressor and another pressure zone.
  • An object of the present disclosure is to provide a scroll compressor that facilitates opening of the bypass passage for capacity adjustment.
  • Another object of the present disclosure is to provide a scroll compressor that reduces the flow damping loss and/or increases the bypass flow area.
  • Another object of the present disclosure is to provide a scroll compressor with a simple and compact structure and capable of adjusting the capacity.
  • a scroll compressor including a movable scroll member, a fixed scroll member, a bypass passage, a sliding member, a bypass control unit, and a biasing member.
  • the movable scroll component has a first end plate and a first scroll blade.
  • the fixed scroll member has a second end plate and a second scroll blade, wherein the second scroll blade is engaged with the first scroll blade to connect the movable scroll member with the fixed scroll blade.
  • a plurality of compression cavities are formed between the components to compress the working fluid.
  • the bypass passage fluidly connects one compression chamber of the plurality of compression chambers to the low pressure region of the scroll compressor.
  • the slider is disposed in the bypass channel and is configured to be able to move between a closed position that prevents working fluid from flowing through the bypass channel and an open position that allows working fluid to flow through the bypass channel.
  • the bypass control unit is configured to control the movement of the slider so that when the scroll compressor is required to operate at a high load, the slider is placed in the closed position, and when the scroll compressor is required When the rotary compressor is operating at a low load, the sliding member is placed in the open position.
  • the biasing member is configured to apply a biasing force to the sliding member to assist the movement of the sliding member from the closed position to the open position.
  • the biasing member since the biasing member is provided, it may be advantageous to move the sliding member to the open position to open the bypass passage and to maintain the sliding member in the open position.
  • the biasing member provides the auxiliary force to open the sliding member, which can ensure that the sliding member can still be opened smoothly and stably maintained in the open state when the pressure in the compression chamber is relatively low, so that the compressor can operate in a wide range. Achieve capacity adjustment within the range.
  • the bypass passage is provided in the second end plate of the fixed scroll component.
  • the bypass passage includes: a proximal section, which is in fluid communication with the one compression cavity; and an accommodation section, which extends from the proximal section and is configured to In accommodating the sliding member; and a distal end section, the distal end section extends from the accommodating section and is in fluid communication with the low pressure area.
  • the accommodating section has a diameter larger than that of the proximal section, and the proximal section and the accommodating section are arranged coaxially.
  • the sliding member includes a cylindrical sliding main body part capable of sliding in the accommodating section.
  • the sliding member further includes a filling part.
  • the filling part is configured to be inserted into the proximal section when the sliding member is in the closed position to achieve a closing function. Since the filling part is slidably inserted into the proximal section, the wear problem of the sealing ring provided on the top of the first scroll blade under full load (or high load) conditions can be reduced or avoided.
  • the filling portion integrally extends from the end surface of the sliding body portion.
  • the filling part is detachably connected to the sliding main body part.
  • the filling part when the filling part is detachably connected to the sliding body part, the filling part is connected to the sliding body part by a threaded fastener.
  • the distal end section extends substantially along the radial direction of the fixed scroll member, and the distal end section has a larger size in the circumferential direction of the fixed scroll member. Long shape.
  • the bypass control unit is configured to selectively introduce high-pressure fluid or low-pressure fluid into the accommodating section to control the sliding member under the pressure difference between opposite sides of the sliding member. exercise.
  • the bypass control unit includes a control valve, a high-pressure channel, a low-pressure channel, and a communication channel.
  • the control valve has a first port, a second port, and a third port.
  • the control valve is configured to switch between a first position that connects the first port to the third port and a second position that connects the second port to the third port.
  • the high-pressure passage communicates the high-pressure region of the scroll compressor to the first port.
  • the low-pressure passage communicates the low-pressure area of the scroll compressor to the second port.
  • the communication passage connects the accommodating section to the third port.
  • control valve is an electromagnetic control valve.
  • the control valve is mounted to the fixed scroll component.
  • the fixed scroll component includes a fixed scroll main body and a cover that are detachably connected.
  • the high-pressure passage, the low-pressure passage, and the communication passage are all arranged in the cover plate and/or the fixed scroll main body.
  • the first scroll blade has two movable scroll blades arranged symmetrically or asymmetrically with respect to the central axis of the movable scroll member, and the second scroll blade has Two fixed scroll blades arranged symmetrically or asymmetrically on the central axis of the fixed scroll component.
  • the scroll compressor further includes: at least one adjustment passage, and each adjustment passage in the at least one adjustment passage connects one compression chamber of the plurality of compression chambers to the scroll The discharge area of the compressor; and at least one one-way valve, each of the at least one one-way valve is configured to only allow the working fluid in a corresponding one of the compression chambers to flow in the corresponding one of the compression chambers When the pressure is greater than a predetermined pressure, it is discharged to the exhaust area.
  • the biasing member is a permanent magnet.
  • the permanent magnet may be fixed to the cover plate of the fixed scroll or the main body of the fixed scroll of the scroll compressor. Since the permanent magnet is arranged above the sliding member, the permanent magnet will not block the flow channel, so the flow area of the working fluid can be increased and the flow resistance can be reduced.
  • the biasing member is an elastic member.
  • the sliding member may have a flange engaged with the elastic member, and the elastic member is provided on the radially outer side of the sliding member.
  • Fig. 1 schematically shows a longitudinal sectional view of a scroll compressor according to an embodiment of the present disclosure, in which the bypass passage is in a closed state;
  • FIG. 2 is a schematic cross-sectional view of the double scroll structure of the compression mechanism of the scroll compressor of FIG. 1;
  • Figure 3 is a partial enlarged cross-sectional view of a capacity adjustment mechanism according to an embodiment of the present disclosure
  • Figure 4 is an exploded perspective view of the fixed scroll component of Figure 3;
  • Figures 5a and 5b respectively show the full-load working and part-load working states of the scroll compressor
  • Fig. 6 schematically shows a partial longitudinal sectional view of a scroll compressor according to another embodiment of the present disclosure, in which the bypass passage is in a closed state;
  • Fig. 7 is an enlarged schematic view of the sliding member of Fig. 6;
  • Figure 8 is an exploded perspective view of the sliding member of Figure 7;
  • Figure 9 is a partial cross-sectional view including the sliding member shown in Figures 7 and 8;
  • Figure 10 is a partial cross-sectional view including the sliding member shown in Figures 1 and 2;
  • FIG. 11 is a front view of a main body of a fixed scroll according to an embodiment of the present disclosure, which shows a distal end section of a bypass channel;
  • Figure 12 is a schematic cross-sectional view of Figure 11.
  • FIG. 13 is a schematic diagram showing the flow area when the bypass channel is opened according to the present disclosure.
  • the scroll compressor 100 may include a substantially closed housing 110, and a motor 120, a drive shaft 130, a main bearing housing 140, and a compression mechanism CM disposed in the housing 110.
  • the housing 110 may include a substantially cylindrical main housing part 111, a top cover 112 provided at the upper end of the main housing part 111, and a bottom cover 113 provided at the lower end of the main housing part 111.
  • a spacer 101 is provided between the top cover 112 and the main housing portion 111, and the spacer 101 divides the internal space of the housing 110 into a suction pressure zone and an exhaust pressure zone.
  • the suction pressure area is defined by the spacer 101, the main housing portion 111, the compression mechanism CM, and the bottom cover 113.
  • An air inlet connector 102 for sucking in low temperature and low pressure working fluid is provided in the suction pressure zone. Therefore, the suction pressure region can also be referred to as the low-pressure side region.
  • the exhaust pressure zone is defined by the spacer 101, the compression mechanism CM, and the top cover 112.
  • An exhaust joint 103 for discharging the compressed high-temperature and high-pressure working fluid is provided in the exhaust pressure zone.
  • the exhaust pressure zone can also be called the high-pressure side zone.
  • the motor 120 may include a stator 121 and a rotor 122.
  • the stator 121 can be fixed with respect to the housing 110 in any suitable manner.
  • the rotor 122 is disposed on the radially inner side of the stator 121 and can rotate in the stator 121 when energized.
  • the drive shaft 130 extends through the rotor 122 and can rotate together with the rotor 122.
  • the upper end of the drive shaft 130 is supported by the main bearing housing 140 via the main bearing, and the lower end is supported by the lower bearing housing 104 via the lower bearing.
  • Both the main bearing housing 140 and the lower bearing housing 104 are fixedly connected to the main housing portion 111 of the housing 110.
  • the compression mechanism CM is supported by the main bearing housing 140 and includes a fixed scroll part 150 and a movable scroll part 160.
  • the fixed scroll component 150 may be fixed relative to the housing 110 in any suitable manner, for example, fixed to the main bearing housing 140 by bolts.
  • the fixed scroll component 150 may be mounted to the housing 110 in a manner that allows the fixed scroll component to move slightly axially relative to the housing 110 to provide axial flexibility.
  • An eccentric crank pin 131 is formed at one end of the drive shaft 130 (the upper end in FIG. 1), and the eccentric crank pin 131 is fitted with and drives the hub 165 of the movable scroll component 160 via an unloading bush and/or a drive bearing (not shown) , So that the movable scroll part 160 rotates in translation relative to the fixed scroll part 150 (that is, the central axis of the movable scroll part 160 rotates around the central axis of the fixed scroll part 150, but the movable scroll part 160 itself does not rotate around itself The central axis of rotation).
  • the movable scroll component 160 includes a first end plate 161 and a spiral first scroll blade 162 extending from the first end plate 161.
  • the fixed scroll component 150 includes a second end plate 151, a spiral second scroll blade 152 extending from the second end plate 151, and a discharge port (not shown) that allows the compressed working fluid to be discharged.
  • the first scroll blade 162 and the second scroll blade 152 are in meshing engagement to form a plurality of compression cavities between the movable scroll part 160 and the fixed scroll part 150 to compress the working fluid.
  • the compression chamber located at the radially outermost side and at suction pressure is called the low-pressure chamber, and the radially innermost compression chamber at the exhaust pressure is called the high-pressure chamber; the pressure is between the low-pressure chamber and the high-pressure chamber.
  • the compression cavity between the cavities is called the medium pressure cavity.
  • the fixed scroll component 150 includes a fixed scroll main body portion 150 a and a cover plate 150 b.
  • the fixed scroll main body 150a includes the second end plate 151 and the second scroll blade 152 described above.
  • the cover plate 150b is connected to the second end plate 151 of the fixed scroll main body 150a in a detachable manner (for example, screws).
  • the fixed scroll component 150 shown in FIG. 1 is a split structure. However, it should be understood that the structure of the fixed scroll component 150 is not limited to the two-piece structure shown in FIG. 1, and may be a one-piece structure, for example.
  • FIG. 2 is a cross-sectional view of the double scroll structure of the compression mechanism CM of the scroll compressor 100 of FIG. 1.
  • the fixed scroll member 150 and the movable scroll member 160 of the scroll compressor 100 each have two scroll blades, and thus are also referred to as a double scroll structure.
  • the first scroll blade 162 of the movable scroll part 160 includes two movable scroll blades 162a and 162b
  • the second scroll blade 152 of the fixed scroll part 150 includes two fixed scroll blades 152a and 152b.
  • the two movable scroll blades 162 a and 162 b may be arranged symmetrically or asymmetrically with respect to the central axis of the movable scroll component 160.
  • the two fixed scroll blades 152a and 152b may be arranged symmetrically or asymmetrically with respect to the central axis of the fixed scroll member 150.
  • the orbiting scroll blade 162a is meshingly engaged with the two fixed scroll blades 152a and 152b to form a first compression chamber group C1.
  • the orbiting scroll blade 162b is in meshing engagement with the two fixed scroll blades 152a and 152b to form a second compression chamber group C2.
  • the first compression chamber group C1 and the second compression chamber group C2 perform compression operations independently of each other and include respective intake ports and exhaust ports.
  • the first compression chamber group C1 and the second compression chamber group C2 may have a common intake port and a common exhaust port.
  • the scroll compressor 100 further includes a capacity adjustment mechanism CR.
  • the capacity adjustment mechanism CR is configured so that the scroll compressor can be switched between a full load operation mode and a partial load operation mode.
  • the full-load operation mode all working fluids in the compression chamber are compressed and discharged from the discharge port.
  • the part-load operation mode a certain compression chamber is bypassed to the low-pressure area, so that the bypassed compression chamber basically does not compress the working fluid, so that the compressor displacement and power consumption can be reduced.
  • the capacity adjustment mechanism CR includes a bypass passage BP that fluidly connects a compression chamber (for example, a medium-pressure chamber) to the low-pressure area, a slider 180 provided in the bypass passage and used to open or close the bypass passage, and a pair of sliders. The 180 movement is controlled by the bypass control unit BC.
  • a compression chamber for example, a medium-pressure chamber
  • the bypass passage BP is provided in the second end plate 151 of the fixed scroll component 150.
  • the bypass passage BP includes a proximal section 171 connected to a compression chamber, a receiving section 172 extending from the proximal section 171 and for receiving the slider 180, and a receiving section 172 extending from the receiving section 172 and fluidly connected to the low pressure The distal section 173 of the area.
  • the sliding member 180 can slide in the accommodating section 172, as shown in the figure up and down.
  • the sliding member 180 is located in the lower position, that is, the closed position. In this closed position, the slider 180 abuts and covers the outlet of the proximal section 171, thereby preventing the working fluid from flowing through the bypass channel BP.
  • the sliding member 180 is in the closed position shown in Figs. 3 and 5a.
  • the sliding member 180 is located in the upper position, that is, the open position. In this open position, the sliding member 180 is away from the proximal section 171, thereby allowing the working fluid in the compression cavity to flow into the containing section 172 via the proximal section 171, and then to discharge to the low pressure area via the distal section 173.
  • the proximal section 171 may be arranged coaxially with the accommodating section 172. That is, the central axis of the proximal section 171 coincides with the central axis of the accommodating section 172.
  • the size (or diameter) of the accommodating section 172 may be larger than the size (or diameter) of the proximal section 171 so as to accommodate the sliding member 180.
  • a step portion for supporting the slider 180 is formed between the accommodating section 172 and the proximal section 171.
  • the sliding member 180 may be substantially cylindrical.
  • the columnar sliding member 180 is simple to manufacture and therefore the manufacturing cost can be reduced.
  • the cylindrical slider 180 allows the proximal section 171 to have a larger diameter (or size).
  • a sealing member 175, for example, a sealing ring, may be provided between the sliding member 180 and the accommodating section 172.
  • a recess for accommodating the sealing member 175 is provided on the outer peripheral surface of the sliding member 180.
  • the end plate 151 may be provided with a recess for accommodating the sealing member 175.
  • the sealing member 175 divides the accommodating section 172 into an upper space and a lower space.
  • the lower space connects the proximal section 171 to the distal section 173.
  • the upper space may receive high-pressure fluid or low-pressure fluid from the bypass control unit BC to form a pressure difference between opposite sides of the sliding member 180, thereby controlling the movement of the sliding member 180.
  • the bypass control unit BC is configured to: when the scroll compressor 100 is running at full load (or high load), the slider 180 is in the closed position shown in FIGS. 3 and 5a, and when the scroll compressor is partly loaded (or During low-load operation, the sliding member 180 is placed in the open position shown in Fig. 5b for pressure relief.
  • the bypass control unit BC includes a control valve 190, a high-pressure passage (not shown), a low-pressure passage (not shown), and a communication passage 193.
  • the control valve 190 has a first port, a second port, and a third port.
  • the control valve 190 can switch between a first position that connects the first port to the third port and a second position that connects the second port to the third port. That is, the control valve 190 can selectively control one of the first port and the second port to communicate with the third port.
  • the high-pressure passage connects the high-pressure area of the scroll compressor to the first port of the control valve 190.
  • the low-pressure passage connects the low-pressure area of the scroll compressor to the second port of the control valve 190.
  • the communication passage 193 connects the accommodating section 172 to the third port of the control valve 190.
  • control valve 190 introduces the high-pressure fluid in the high-pressure region or the low-pressure fluid in the low-pressure region to the upper portion of the accommodating section 172 via the communication passage 193 by selectively controlling the first port or the second port to communicate with the third port. In space.
  • FIG. 5a shows the slider 180 in the closed position.
  • the control valve 190 is in the first position that connects the first port to the third port.
  • the control valve 190 allows the high-pressure fluid to flow through the control valve 190 and be introduced into the upper space of the accommodating section 172 via the communication passage 193. Since the pressure of the high-pressure fluid is greater than the intermediate pressure of the fluid in the compression chamber communicating with the proximal section 171, the high-pressure fluid forces the slider 180 to abut and cover the proximal end 171 to close the bypass passage BP.
  • FIG. 5b shows the slider 180 in the open position.
  • the control valve 190 is in the second position that connects the second port to the third port.
  • the control valve 190 allows the low-pressure fluid to flow through the control valve 190 and be introduced into the upper space of the accommodating section 172 via the communication passage 193. Since the pressure of the low-pressure fluid is lower than the medium pressure of the fluid in the compression chamber communicating with the proximal section 171, the fluid in the compression chamber forces the slider 180 to slide upward to abut the cover plate 150b to open the bypass passage BP.
  • the control valve 190 may be, for example, an electromagnetic control valve, or may be any other suitable type of valve.
  • the control valve 190 is installed to the fixed scroll member 150. In the examples shown in FIGS. 4, 5a, and 5b, the control valve 190 is mounted on the outer peripheral surface of the fixed scroll main body 150a. In this way, the piping provided on the outside of the compressor housing 110 can be omitted, thereby reducing the volume of the compressor.
  • the capacity adjustment mechanism CR further includes an elastic member 181, for example, a spring.
  • the elastic member 181 is configured to apply a biasing force to the slider 180 to assist the slider 180 to move from the closed position to the open position.
  • the sliding member 180 can be conveniently and reliably opened, and at the same time, the sliding member 180 can be maintained at the open position.
  • the elastic member 181 provides auxiliary biasing force, when the sliding member 180 is moved to the open position, the flow damping loss of the working fluid can be reduced.
  • a flange may be provided on the outer peripheral surface of the sliding member 180 so that the elastic member 181 is located between the flange and the step portion for supporting the sliding member 180 (as described above, between the accommodating section 172 and the proximal section 171 Formed between the steps). It should be understood that the arrangement of the elastic member 181 is not limited to the specific example shown, but can be changed.
  • FIG. 6 shows a capacity adjustment mechanism CR according to another embodiment of the present disclosure.
  • the example in FIG. 6 is different from the example in FIG. 3 in that the biasing member is different and the structure of the sliding member is different.
  • the different parts from the example of FIG. 3 will be described in detail below, and the same parts will not be repeated.
  • the biasing member that provides the biasing force is implemented as an elastic member 181
  • the biasing member in the example of FIG. 6, is implemented as a permanent magnet 281.
  • the slider 280 is formed of a magnetic material.
  • the permanent magnet 281 applies an attractive force to the slider 280 to assist the slider 280 to move from the closed position to the open position.
  • the permanent magnet 281 can provide similar advantages to the elastic member 181.
  • the permanent magnet 281 is provided above the slider 280.
  • the permanent magnet 281 may be installed to the cover plate 150b or to the end plate 151 of the fixed scroll main body portion 150a.
  • the cover plate 150b or the end plate 151 may be provided with a recess for accommodating the permanent magnet 281.
  • the permanent magnet 281 is disposed above the sliding member 280, it does not occupy the flow area below the sliding member 280, and therefore, the flow damping loss of the working fluid can be further reduced. Since the permanent magnet 281 is provided, the height of the sliding member 280 can be reduced, so that the stroke of the sliding member 280 becomes larger, thereby increasing the flow area of the working fluid.
  • the sliding member 280 includes a sliding main body part 283 and a filling part 284.
  • the sliding main body part 283 is slidably received in the receiving section 172, and has a shape matching the receiving section 172, for example, a cylindrical shape.
  • the filling part 284 can be inserted into the proximal section 271.
  • the filling portion 284 leaves the proximal section 271 to allow the working fluid in the compression cavity to flow out.
  • the sliding body part 283 and the filling part 284 are provided separately and then connected together.
  • the filling part 284 is detachably connected to the sliding body part 283 by a threaded fastener 278.
  • the sliding body portion 283 has a central hole 285 for receiving the threaded fastener 278 and a protrusion 288 for stopping the large-size head 278 a of the threaded fastener 278.
  • the filling part 284 has an internal thread part 287 engaged with the external thread part 278 b of the threaded fastener 278.
  • a sealing member 276, for example, a sealing ring, may be provided between the sliding main body part 283 and the filling part 284.
  • the filling part 284 is provided with a recess 286 for accommodating the sealing member 276. As shown in FIG. In an alternative example, a recess for accommodating the sealing member 276 may be provided on the sliding body part 283.
  • the bottom end surface (ie, the sealing surface) of the sliding body 283 needs to be sealed with the fixed scroll component 150. Therefore, the separate arrangement of the sliding body portion 283 and the filling portion 284 can make the bottom end surface of the sliding body portion 283 get a good grinding process, realize a good seal with the fixed scroll component 150, and help improve the performance of the compressor. .
  • FIG. 9 shows that the slider 280 shown in FIGS. 7 and 8 is assembled to the fixed scroll component 150.
  • a sealing ring 163 is provided on the top of the first scroll blade 162 of the movable scroll component 160.
  • the first scroll blade 162 of the movable scroll component 160 and the second end plate 151 of the fixed scroll component 150 (or the fixed scroll main body 150a) are sealed by the sealing ring 163 In order to prevent the working fluid in one compression cavity from leaking into another compression cavity.
  • the filling portion 284 When the slider 280 is in the closed position, the filling portion 284 is inserted into the proximal section 271 and abuts against the top of the first scroll blade 162 of the movable scroll component 160 via the sealing ring 163. Therefore, under full load (or high load) conditions, the filling portion 284 is inserted into the proximal section 271, which can reduce or avoid the wear problem of the sealing ring 163.
  • FIG. 10 shows an example in which the sliding main body part 383 and the filling part 384 are integrated.
  • the filling portion 384 integrally extends from the end surface of the sliding body portion 383.
  • the step for assembling the filling part 384 to the sliding body part 383 can be omitted, and the installation procedure can be simplified.
  • the sliding main body 383 and the filling part 384 are an integral piece, a rounded corner is formed at the transition T between the outer peripheral surface of the sliding main part 383 and the filling part 384 during processing.
  • the split sliders in FIGS. 7 and 8 can avoid the rounded corners.
  • a right angle is formed at the transition T between the sliding body part 283 and the outer peripheral surface of the filling part 284, rather than a rounded corner. Therefore, the interference between the sliding part and the fixed scroll part can be avoided, the sealing performance between the sliding part and the fixed scroll part can be improved, the leakage of the working fluid can be reduced, and the performance of the compressor can be improved.
  • FIGS 11 and 12 show an example of the distal end section of the bypass channel.
  • the distal end section 173 extends substantially in the radial direction of the fixed scroll component 150.
  • the distal end section 173 has a relatively large size in the circumferential direction of the fixed scroll component 150 and has an elongated shape.
  • the long-shaped distal section can significantly increase the flow area of the working fluid. As a result, the flow damping loss can be reduced and the bypass performance can be improved.
  • Figure 13 shows the slider in the open position. Combining Fig. 13 with Fig. 11 and Fig. 12, the ability of the elongated distal section to increase the flow area can be easily understood.
  • the scroll compressor 100 may further include at least one regulating passage provided in the fixed scroll component 150 (the fixed scroll main body portion 150a) and at least one single unit for controlling the opening or closing of the regulating passage.
  • Each regulating passage connects a compression chamber to the discharge area of the scroll compressor.
  • Each one-way valve VVR is configured to only allow the working fluid in the corresponding compression chamber to be discharged to the exhaust area when the pressure in the corresponding compression chamber is greater than a predetermined pressure.
  • variable pressure ratio of the scroll compressor By setting the one-way valve VVR, the variable pressure ratio of the scroll compressor can be realized. According to requirements, a variable pressure ratio adjustment mechanism (adjustment channel and one-way valve VVR) can be combined with the above-mentioned capacity adjustment mechanism CR to obtain the required adjustment capacity and performance.
  • the on-off time of the bypass passage BP can be controlled by pulse modulation, thereby controlling the capacity of the scroll compressor.
  • a bypass passage BP can be provided in any compression chamber group C1 or C2 to achieve, for example, 50% of the capacity. It should be understood that, for a compression mechanism with a double scroll structure, a 50%-100% capacity adjustment can also be achieved in conjunction with the control of the on-off time of the bypass passage BP.
  • multiple bypass passages communicating with different compression chambers may be provided to achieve different capacity adjustments.

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Abstract

一种涡旋压缩机（100），包括动涡旋部件（160）、定涡旋部件（150）、旁通通道（BP）、滑动件（180）、旁通控制单元（BC）以及偏置件（181）。动涡旋部件（160）的第一涡旋叶片（162）与定涡旋部件（150）的第二涡旋叶片（152）之间形成多个压缩腔以便对工质进行压缩。旁通通道（BP）将多个压缩腔中的一个压缩腔流体连通至涡旋压缩机（100）的低压区域。滑动件（180）设置在旁通通道（BP）中并且构造成能够在防止工质流过旁通通道（BP）的关闭位置与允许工质流过旁通通道（BP）的打开位置之间运动。旁通控制单元（BC）构造成对滑动件（180）的运动进行控制，使得当需要涡旋压缩机（100）高负荷运行时，使滑动件（180）处于关闭位置，而当需要涡旋压缩机（100）低负荷运行时，使滑动件（180）处于打开位置。偏置件（181）构造成对滑动件施加偏置力以辅助滑动件从关闭位置运动至打开位置。

Description

涡旋压缩机
本申请要求于2019年12月20日提交中国专利局的申请号为201911332973.4、发明名称为“涡旋压缩机”的中国专利申请的优先权。该专利申请的全部内容通过引用结合在本申请中。
技术领域
本公开涉及涡旋压缩机技术领域，更具体地，涉及能够调节容量的涡旋压缩机。
背景技术
本部分的内容仅提供了与本公开相关的背景信息，其可能并不构成现有技术。
已知的是，涡旋压缩机属于容量式压缩的压缩机械。涡旋压缩机的压缩机构通常包括定涡旋部件和动涡旋部件。容量调节技术是制冷及热泵系统发展的一个重要方向，可以使得机组输出能力更好适应末端负荷需求，减少机组开停机，提升系统能效和舒适性。已知有的压缩机包括多种容量调节机构以改变压缩机的操作容量。容量调节机构可以用于在满负载条件或部分负载条件下操作压缩机。满负载变化或部分负载变化的需求取决于季节变化、被调节空间中的占据者和/或制冷单元负载要求。
典型地，容量调节机构可以包括延伸穿过涡旋部件的流体通道以选择性地提供压缩机的压缩腔与另一压力区之间的流体连通。例如，在制冷系统的应用中，为了解决部分负荷冷量的需求，往往通过旁通涡旋叶片的部分型线，使涡旋部件的压比变小，以达到调节压缩机的工作容量的目的，进而与部分负荷冷量更好地匹配。
发明内容
本公开的一个目的在于提供一种有利于打开旁通通道以便容量调节的涡旋压缩机。
本公开的另一个目的在于提供一种减小流动阻尼损失和/或增加旁通流通面积的涡旋压缩机。
本公开的另一个目的在于提供一种结构简单且紧凑的能够调节容量的涡旋压缩机。
根据本公开的一个方面，提供了一种涡旋压缩机，其包括动涡旋部件、定涡旋部件、旁通通道、滑动件、旁通控制单元以及偏置件。所述动涡旋部件具有第一端板和第一涡旋叶片。所述定涡旋部件具有第二端板和第二涡旋叶片，其中，所述第二涡旋叶片与所述第一涡旋叶片接合以在所述动涡旋部件与所述定涡旋部件之间形成多个压缩腔以便对工质进行压缩。所述旁通通道将所述多个压缩腔中的一个压缩腔流体连通至所述涡旋压缩机的低压区域。所述滑动件设置在所述旁通通道中并且构造成能够在防止工质流过所述旁通通道的关闭位置与允许工质流过所述旁通通道的打开位置之间运动。所述旁通控制单元构造成对所述滑动件的运动进行控制，使得：当需要所述涡旋压缩机高负荷运行时，使所述滑动件处于所述关闭位置，而当需要所述涡旋压缩机低负荷运行时，使所述滑动件处于所述打开位置。所述偏置件构造成对所述滑动件施加偏置力以辅助所述滑动件从所述关闭位置运动至所述打开位置。
在根据本公开的涡旋压缩机中，由于设置有偏置件，可以有利于将滑动件移动至打开位置以打开旁通通道且有利于将滑动件保持在打开位置中。偏 置件提供了打开滑动件的辅助力，可以确保在压缩腔内压力相对较低的情况下，滑动件依然可以顺利的打开并稳定的保持在打开状态，使压缩机可以在较宽的运行范围内实现容量调节。
在一些实施方式中，所述旁通通道设置在所述定涡旋部件的第二端板中。所述旁通通道包括：近端部段，所述近端部段流体连通至所述一个压缩腔；容置部段，所述容置部段从所述近端部段延伸并构造成用于容置所述滑动件；以及远端部段，所述远端部段从所述容置部段延伸并且流体连通至所述低压区域。
在一些实施方式中，所述容置部段具有比所述近端部段的直径大的直径，并且所述近端部段与所述容置部段同轴设置。
在一些实施方式中，所述滑动件包括能够在所述容置部段中滑动的柱状的滑动主体部。
在一些实施方式中，所述滑动件还包括填充部。所述填充部构造成：当所述滑动件处于所述关闭位置时插入所述近端部段中，以实现关闭功能。由于填充部可滑动地插入所述近端部段中，因此可以减轻或避免设置在第一涡旋叶片的顶部上的密封圈在全负荷(或高负荷)工况下的磨损问题。
在一些实施方式中，所述填充部从所述滑动主体部的端面一体地延伸。或者，所述填充部以可拆卸的方式连接至所述滑动主体部。
在一些实施方式中，在所述填充部以可拆卸的方式连接至所述滑动主体部的情况下，所述填充部通过螺纹紧固件连接至所述滑动主体部。
在一些实施方式中，所述远端部段基本上沿所述定涡旋部件的径向方向延伸，并且所述远端部段具有在所述定涡旋部件的圆周方向上尺寸较大的长 形形状。
在一些实施方式中，所述旁通控制单元构造成选择性地向所述容置部段中引入高压流体或低压流体以在所述滑动件的相对两侧的压差下控制所述滑动件的运动。
在一些实施方式中，所述旁通控制单元包括控制阀、高压通道、低压通道和连通通道。所述控制阀具有第一端口、第二端口和第三端口。所述控制阀构造成在将所述第一端口连通至所述第三端口的第一位置与将所述第二端口连通至所述第三端口的第二位置之间切换。所述高压通道将所述涡旋压缩机的高压区域连通至所述第一端口。所述低压通道将所述涡旋压缩机的低压区域连通至所述第二端口。所述连通通道将所述容置部段连通至所述第三端口。
在一些实施方式中，所述控制阀是电磁控制阀。所述控制阀安装至所述定涡旋部件。
在一些实施方式中，所述定涡旋部件包括以可拆卸的方式连接的定涡旋主体部和盖板。所述高压通道、所述低压通道和所述连通通道均设置在所述盖板和/或所述定涡旋主体部中。
在一些实施方式中，所述第一涡旋叶片具有关于所述动涡旋部件的中心轴线对称或不对称地布置的两个动涡旋叶片，并且所述第二涡旋叶片具有关于所述定涡旋部件的中心轴线对称或不对称地布置的两个定涡旋叶片。
在一些实施方式中，所述涡旋压缩机还包括：至少一个调节通道，所述至少一个调节通道中的每个调节通道将所述多个压缩腔中的一个压缩腔连通至所述涡旋压缩机的排气区域；以及至少一个单向阀，所述至少一个单向阀 中的每个单向阀构造成仅允许相应的一个压缩腔中的工质在该相应的一个压缩腔中的压力大于预定压力时排出至所述排气区域。
在一些实施方式中，所述偏置件为永磁体。所述永磁体可以固定至所述涡旋压缩机的定涡旋的盖板或定涡旋主体中。由于永磁体设置在滑动件的上方，使得永磁体不会阻挡流动通道，因此可以增大工质的流通面积以及减小流动阻力。
在一些实施方式中，所述偏置件为弹性件。所述滑动件可以具有与所述弹性件接合的凸缘，所述弹性件设置在所述滑动件的径向外侧。
通过本文提供的说明，其他的应用领域将变得显而易见。应该理解，本部分中描述的特定示例和实施方式仅处于说明目的而不是试图限制本公开的范围。
附图说明
通过以下参照附图的描述，本公开的一个或几个实施方式的特征和优点将变得更加容易理解，在附图中：
图1示意性地示出了根据本公开实施方式的涡旋压缩机的纵向剖视图，其中，旁通通道处于关闭状态；
图2是图1的涡旋压缩机的压缩机构的双涡卷结构的横截面示意图；
图3是根据本公开实施方式的容量调节机构的局部放大剖视图；
图4是图3的定涡旋部件的分解立体图；
图5a和图5b分别示出了涡旋压缩机的满负荷工作和部分负荷工作状态；
图6示意性地示出了根据本公开另一实施方式的涡旋压缩机的局部纵向 剖视图，其中，旁通通道处于关闭状态；
图7是图6的滑动件的放大示意图；
图8是图7的滑动件的分解立体图；
图9是包括图7和图8所示的滑动件的局部剖视图；
图10是包括图1和图2所示的滑动件的局部剖视图；
图11是根据本公开实施方式的定涡旋主体部的正视图，其示出了旁通通道的远端部段；
图12是图11的横截面示意图；以及
图13是示出根据本公开的旁通通道打开时的流通面积的示意图。
附图中对应的附图标记始终指示相同的或对应的部件和特征。
具体实施方式
现在将参照附图更全面地描述示例性实施方式。
提供示例性实施方式以使得本公开将是详尽的并且将向本领域技术人员更全面地传达范围。阐述了许多具体细节比如具体部件、装置和方法的示例，以提供对本公开的各实施方式的透彻理解。对本领域技术人员而言将清楚的是，不需要采用具体细节，示例性实施方式可以以许多不同的形式实施，并且也不应当理解为限制本公开的范围。在一些示例性实施方式中，不对公知的过程、公知的装置结构和公知的技术进行详细的描述。
下面参见图1将描述根据本公开的涡旋压缩机100的整体结构。应理解的是，本公开的教导不局限于图1所示的涡旋压缩机，而是可以适用于多种不同类型的涡旋式压缩机中。
如图1所示，涡旋压缩机100可以包括大体封闭的壳体110以及设置在 壳体110内的马达120、驱动轴130、主轴承座140和压缩机构CM。
壳体110可以包括大致圆筒形的主壳体部111、设置在主壳体部111的上端处的顶盖112以及设置在主壳体部111的下端处的底盖113。在顶盖112和主壳体部111之间设置有间隔件101，间隔件101将壳体110的内部空间分隔成吸气压力区和排气压力区。
由间隔件101、主壳体部111、压缩机构CM和底盖113限定吸气压力区。在吸气压力区设置有用于吸入低温低压工质的进气接头102。由此，吸气压力区也可以称为低压侧区域。
由间隔件101、压缩机构CM和顶盖112限定排气压力区。在排气压力区设置有用于排出压缩后的高温高压工质的排气接头103。而排气压力区也可以称为高压侧区域。
马达120可以包括定子121和转子122。定子121可以采用任何合适的方式相对于壳体110固定。转子122设置在定子121的径向内侧，并且通电时能够在定子121中旋转。
驱动轴130延伸穿过转子122而能够随转子122一起做旋转运动。驱动轴130的上端经由主轴承由主轴承座140支撑，下端经由下轴承由下轴承座104支撑。主轴承座140和下轴承座104均固定连接至壳体110的主壳体部111。
压缩机构CM由主轴承座140支承并且包括定涡旋部件150和动涡旋部件160。定涡旋部件150可以以任何合适的方式相对于壳体110固定，例如通过螺栓固定于主轴承座140。或者，定涡旋部件150可以以允许定涡旋部件相对于壳体110略微轴向移动以提供轴向柔性的方式安装至壳体110。
在驱动轴130的一端(图1中的上端)形成有偏心曲柄销131，偏心曲柄销131经由卸载衬套和/或驱动轴承(未示出)配合并驱动动涡旋部件160的毂部165，使得动涡旋部件160相对于定涡旋部件150平动转动(即，动涡旋部件160的中心轴线绕定涡旋部件150的中心轴线旋转，但是动涡旋部件160本身不会绕自身的中心轴线旋转)。
动涡旋部件160包括第一端板161和从所述第一端板161延伸的螺旋形的第一涡旋叶片162。定涡旋部件150包括第二端板151、从所述第二端板151延伸的螺旋形的第二涡旋叶片152和允许压缩的工质排出的排出口(未示出)。第一涡旋叶片162与第二涡旋叶片152啮合地接合以在动涡旋部件160与定涡旋部件150之间形成多个压缩腔以便对工质进行压缩。
在本文中，将位于径向最外侧并且处于吸气压力的压缩腔称为低压腔，将位于径向最内侧并且处于排气压力的压缩腔称为高压腔；将压力介于低压腔和高压腔之间的压缩腔称为中压腔。随着涡旋压缩机的运行，工质从径向最外侧的低压腔沿着涡旋叶片的型线经由径向内侧的体积逐渐减小的各个中压腔，最终到达径向最内侧的高压腔，同时被压缩成高温高压工质。压缩工质再经由排出口排出压缩机构。
在图1的示例中，定涡旋部件150包括定涡旋主体部150a和盖板150b。定涡旋主体部150a包括上述第二端板151和第二涡旋叶片152。盖板150b以可拆卸的方式(例如，螺钉)连接至定涡旋主体部150a的第二端板151。图1中所示的定涡旋部件150是分体式结构。然而，应理解的是，定涡旋部件150的结构不局限于图1中所示的两件式结构，例如可以是一体式结构。
图2是图1的涡旋压缩机100的压缩机构CM的双涡卷结构的横截面图。 如图2所示，涡旋压缩机100的定涡旋部件150和动涡旋部件160各自具有两个涡旋叶片，由此也被称为双涡卷结构。具体地，动涡旋部件160的第一涡旋叶片162包括两个动涡旋叶片162a和162b，并且定涡旋部件150的第二涡旋叶片152包括两个定涡旋叶片152a和152b。两个动涡旋叶片162a和162b可以关于动涡旋部件160的中心轴线对称地布置或者不对称地布置。类似地，两个定涡旋叶片152a和152b可以关于定涡旋部件150的中心轴线对称或不对称地布置。
动涡旋叶片162a与两个定涡旋叶片152a和152b啮合地接合从而形成第一压缩腔组C1。动涡旋叶片162b与两个定涡旋叶片152a和152b啮合地接合从而形成第二压缩腔组C2。第一压缩腔组C1和第二压缩腔组C2彼此独立地进行压缩操作并且包括各自的进气口和排气口。或者，第一压缩腔组C1和第二压缩腔组C2可以具有共同的进气口和共同的排气口。
根据本公开的涡旋压缩机100还包括容量调节机构CR。容量调节机构CR构造成使得涡旋压缩机可以在满负荷运行模式与部分负荷运行模式之间切换。在满负荷运行模式下，所有压缩腔内的工质经过压缩从排出口排出。在部分负荷运行模式下，某个压缩腔旁通至低压区域，使得被旁通的这个压缩腔基本上不会对工质进行压缩，从而能够实现压缩机排量的降低和功耗的降低。
下面参见图3、图4、图5a和图5b对根据本公开实施方式的容量调节机构CR进行描述。容量调节机构CR包括将一个压缩腔(例如，中压腔)流体连通至低压区域的旁通通道BP、设置在旁通通道中且用于打开或关闭旁通通道的滑动件180、对滑动件180的运动进行控制的旁通控制单元BC。
如图所示，旁通通道BP设置在定涡旋部件150的第二端板151中。旁通通道BP包括连通至一个压缩腔的近端部段171、从近端部段171延伸并用于容置滑动件180的容置部段172、以及从容置部段172延伸并且流体连通至低压区域的远端部段173。
滑动件180可以在容置部段172中滑动，如图中的上下滑动。在图3和图5a中，滑动件180位于下方位置，即关闭位置。在该关闭位置，滑动件180抵接并覆盖近端部段171的出口，由此防止工质流过旁通通道BP。当压缩机满负荷运行时，使滑动件180处于图3和图5a所示的关闭位置。
在图5b中，滑动件180位于上方位置，即打开位置。在该打开位置，滑动件180远离近端部段171，从而允许压缩腔中的工质经由近端部段171流入容置部段172，再经由远端部段173泄放至低压区域。
近端部段171可以与容置部段172同轴地设置。即，近端部段171的中心轴线与容置部段172的中心轴线重合。容置部段172的尺寸(或直径)可以大于近端部段171的尺寸(或直径)，以便容置滑动件180。在容置部段172与近端部段171之间形成用于支撑滑动件180的台阶部。滑动件180可以大体呈柱状。柱状的滑动件180的制造简单并因此可以降低制造成本。此外，柱状的滑动件180允许近端部段171可以具有较大的直径(或尺寸)。
可以在滑动件180与容置部段172之间设置有密封件175，例如，密封圈。在滑动件180的外周面上设置有用于容置密封件175的凹部。在替代性示例中，端板151可以设置有用于容置密封件175的凹部。密封件175将容置部段172分为上部空间和下部空间。下部空间将近端部段171连通至远端部段173。上部空间可以接收来自旁通控制单元BC的高压流体或低压流体， 以在滑动件180的相对两侧形成压差，从而控制滑动件180的运动。
旁通控制单元BC构造成：当涡旋压缩机100满负荷(或高负荷)运行时，使滑动件180处于图3和图5a所示的关闭位置，而当涡旋压缩机部分负荷(或低负荷)运行时，使滑动件180处于图5b所示的打开位置以进行泄压。
旁通控制单元BC包括控制阀190、高压通道(未示出)、低压通道(未示出)和连通通道193。控制阀190具有第一端口、第二端口和第三端口。控制阀190能够在将第一端口连通至第三端口的第一位置与将第二端口连通至第三端口的第二位置之间切换。即，控制阀190能够选择性地控制第一端口和第二端口中的一者与第三端口连通。
高压通道将涡旋压缩机的高压区域连通至控制阀190的第一端口。低压通道将涡旋压缩机的低压区域连通至控制阀190的第二端口。连通通道193将容置部段172连通至控制阀190的第三端口。
因此，控制阀190通过选择性地控制第一端口或第二端口与第三端口连通来将高压区域中的高压流体或低压区域中的低压流体经由连通通道193引入至容置部段172的上部空间中。
参见图5a，其示出了滑动件180处于关闭位置。在图5a的示例中，控制阀190位于将第一端口连通至第三端口的第一位置。这样，控制阀190允许高压流体流过控制阀190并经由连通通道193引入至容置部段172的上部空间中。由于高压流体的压力大于与近端部段171连通的压缩腔中的流体的中压压力，因此高压流体迫使滑动件180抵接并覆盖近端端部171以关闭旁通通道BP。
参见图5b，其示出了滑动件180处于打开位置。在图5b的示例中，控 制阀190位于将第二端口连通至第三端口的第二位置。这样，控制阀190允许低压流体流过控制阀190并经由连通通道193引入至容置部段172的上部空间中。由于低压流体的压力小于与近端部段171连通的压缩腔中的流体的中压压力，因此压缩腔中的流体迫使滑动件180向上滑动至抵接盖板150b以打开旁通通道BP。
控制阀190例如可以是电磁控制阀，或者可以是任何其他合适类型的阀。控制阀190安装至定涡旋部件150。在图4、图5a和图5b所示的示例中，控制阀190安装至定涡旋主体部150a的外周面上。这样，可以省去设置在压缩机壳体110的外部的管路设置，从而减小压缩机的体积。
再参见图3，容量调节机构CR还包括弹性件181，例如，弹簧。弹性件181构造成对滑动件180施加偏置力以辅助滑动件180从关闭位置运动至打开位置。通过设置弹性件181，可以便利且可靠地打开滑动件180，同时能够将滑动件180保持在打开位置处。此外，由于弹性件181提供辅助的偏置力，在将滑动件180移动至打开位置时，可以减小工质流动阻尼损失。
滑动件180的外周面上可以设置有凸缘使得弹性件181位于所述凸缘与用于支撑滑动件180的台阶部(如上所述，在容置部段172与近端部段171之间形成的台阶部)之间。应理解的是，弹性件181的设置不局限于图示的具体示例，而是可以改变。
图6示出了根据本公开另一实施方式的容量调节机构CR。图6中的示例与图3中的示例的不同之处在于偏置件不同以及滑动件的结构不同。下面将详细描述与图3的示例不同的部分，相同的部分不再赘述。
在图3的示例中，提供偏置力的偏置件实施为弹性件181，而在图6的 示例中，偏置件实施为永磁体281。滑动件280由磁性材料形成。永磁体281对滑动件280施加吸引力以辅助滑动件280从关闭位置运动至打开位置。永磁体281可以提供与弹性件181相似的优点。
永磁体281设置在滑动件280的上方。永磁体281可以安装至盖板150b或者安装至定涡旋主体部150a的端板151。盖板150b上或者端板151上可以设置有用于容置永磁体281的凹部。在这些示例中，永磁体281因为设置在滑动件280的上方，因而不占用滑动件280下方的流通面积，并因此可以进一步减小工质流动阻尼损失。由于设置有永磁体281，滑动件280的高度可以减小，使得滑动件280的行程变大，从而使得工质的流通面积增加。
参见图7和图8，其分别示出了图6的滑动件280的剖视图和分解立体图。如图所示，滑动件280包括滑动主体部283和填充部284。滑动主体部283以可滑动的方式容置在容置部段172中，具有与容置部段172匹配的形状，例如柱形形状。当滑动件280从打开位置移动至关闭位置时，填充部284能够插入近端部段271中。当滑动件280从关闭位置移动至打开位置时，填充部284离开近端部段271以允许压缩腔中的工质流出。
滑动主体部283与填充部284分开地设置，然后连接在一起。在图示的示例中，通过螺纹紧固件278以可拆卸的方式将填充部284连接至滑动主体部283。
滑动主体部283具有用于容置螺纹紧固件278的中央孔285以及用于止挡螺纹紧固件278的大尺寸头部278a的凸起288。填充部284具有与螺纹紧固件278的外螺纹部278b接合的内螺纹部287。可以在滑动主体部283与填充部284之间设置密封件276，例如，密封圈。在填充部284上设置有用于 容置密封件276的凹部286。在替代性示例中，可以在滑动主体部283上设置用于容置密封件276的凹部。
由于滑动主体部283滑动配合在容置部段272中，滑动主体部283的底端面(即密封面)需要实现与定涡旋部件150之间的密封。因此，滑动主体部283与填充部284的分开设置，可以使滑动主体部283的底端面得到良好的磨削加工，实现与定涡旋部件150之间的良好密封，有助于提高压缩机性能。
图9示出了图7和图8所示的滑动件280装配到定涡旋部件150上。如图9中清楚地示出，在动涡旋部件160的第一涡旋叶片162的顶部上设置有密封圈163。在涡旋压缩机正常运行时，通过密封圈163将动涡旋部件160的第一涡旋叶片162与定涡旋部件150(或者定涡旋主体部150a)的第二端板151之间密封以防止一个压缩腔中的工质泄漏至另一个压缩腔中。当滑动件280处于关闭位置时，填充部284插入近端部段271中，并且经由密封圈163抵接动涡旋部件160的第一涡旋叶片162的顶部。因此在全负荷(或高负荷)工况下，填充部284插入近端部段271中，可以减轻或避免密封圈163的磨损问题。
图10示出了滑动主体部383与填充部384为一体件的示例。在图10的示例中，填充部384从滑动主体部383的端面一体地延伸。在该示例中，可以省去用于将填充部384组装至滑动主体部383的步骤，可以简化安装程序。
在图10的示例中，由于滑动主体部383与填充部384为一体件，因此加工时会在滑动主体部383与填充部384的外周面的过渡处T形成圆角。与图10的示例相比，图7和图8中的分体式的滑动件可以避免该圆角。如图9 中以放大的形式示出的，当将填充部284螺纹连接至滑动主体部283之后，在滑动主体部283与填充部284的外周面的过渡处T形成直角，而非圆角，由此可以避免滑动件与定涡旋部件之间的干涉，提高滑动件与定涡旋部件之间的密封性，减小工质泄漏量，从而提高压缩机的性能。
参见图11和图12，其示出了旁通通道的远端部段的一个示例。如图所示，远端部段173基本上沿定涡旋部件150的径向方向延伸。远端部段173在定涡旋部件150的圆周方向上具有较大尺寸，呈长形形状。与圆孔形式的远端部段相比，长形形状的远端部段能够显著增加工质的流通面积。由此，可以减小流动阻尼损失并提高旁通性能。图13示出了滑动件处于打开位置。将图13与图11和图12结合来看，则可以很容易地理解长形的远端部段的增加流通面积的能力。
再参见图4和图12，涡旋压缩机100还可以包括设置在定涡旋部件150(定涡旋主体部150a)中的至少一个调节通道以及用于控制调节通道打开或关闭的至少一个单向阀VVR。每个调节通道将一个压缩腔连通至涡旋压缩机的排气区域。每个单向阀VVR构造成仅允许相应压缩腔中的工质在相应压缩腔中的压力大于预定压力时排出至排气区域。
通过设置单向阀VVR，可以实现涡旋压缩机的可变压比。根据需要，可以将可变压比调节机构(调节通道和单向阀VVR)与上述容量调节机构CR结合起来，以获得所需的调节容量和性能。
可以通过脉冲调制控制旁通通道BP的通断时间,从而控制涡旋压缩机的容量。在涡旋压缩机的压缩机构为双涡卷结构时，可以在任一个压缩腔组C1或C2中设置旁通通道BP来实现例如50％的容量。应理解的是，对于双涡卷 结构的压缩机构，也可以结合对旁通通道BP的通断时间的控制来实现50％-100％的容量调节。在替代性示例中，可以设置有与不同压缩腔连通的多个旁通通道以实现不同的容量调节。
上文已经具体描述了本公开的各种实施方式和变型，但是本领域技术人员应该理解，本公开并不局限于上述具体的实施方式和变型而是可以包括其他各种可能的组合和结合。在不偏离本公开的实质和范围的情况下可由本领域的技术人员实现其他的变型和变体。所有这些变型和变体都落入本公开的范围内。而且，所有在此描述的构件都可以由其他技术性上等同的构件来代替。

Claims (18)

  1. 一种涡旋压缩机(100)，包括：
    动涡旋部件(160)，所述动涡旋部件具有第一端板(161)和第一涡旋叶片(162)；
    定涡旋部件(150)，所述定涡旋部件具有第二端板(151)和第二涡旋叶片(152)，其中，所述第二涡旋叶片与所述第一涡旋叶片接合以在所述动涡旋部件与所述定涡旋部件之间形成多个压缩腔以便对工质进行压缩；
    旁通通道(BP)，所述旁通通道将所述多个压缩腔中的一个压缩腔流体连通至所述涡旋压缩机的低压区域；
    滑动件(180)，所述滑动件设置在所述旁通通道中并且构造成能够在防止工质流过所述旁通通道的关闭位置与允许工质流过所述旁通通道的打开位置之间运动；
    旁通控制单元(BC)，所述旁通控制单元构造成对所述滑动件的运动进行控制，使得：当需要所述涡旋压缩机高负荷运行时，使所述滑动件处于所述关闭位置，而当需要所述涡旋压缩机低负荷运行时，使所述滑动件处于所述打开位置；以及
    偏置件(190)，所述偏置件构造成对所述滑动件施加偏置力以辅助所述滑动件从所述关闭位置运动至所述打开位置。
  2. 根据权利要求1所述的涡旋压缩机，其中，所述旁通通道设置在所述定涡旋部件的第二端板中，所述旁通通道包括：
    近端部段(171)，所述近端部段流体连通至所述一个压缩腔；
    容置部段(172)，所述容置部段从所述近端部段延伸并构造成用于容置 所述滑动件；以及
    远端部段(173)，所述远端部段从所述容置部段延伸并且流体连通至所述低压区域。
  3. 根据权利要求2所述的涡旋压缩机，其中，所述容置部段具有比所述近端部段的直径大的直径，并且所述近端部段与所述容置部段同轴设置。
  4. 根据权利要求3所述的涡旋压缩机，其中，所述滑动件包括能够在所述容置部段中滑动的柱状的滑动主体部(283、383)。
  5. 根据权利要求4所述的涡旋压缩机，其中，所述滑动件还包括填充部(284、384)，所述填充部构造成：当所述滑动件处于所述关闭位置时插入所述近端部段中，以及当所述滑动件处于所述打开位置时离开所述近端部段。
  6. 根据权利要求5所述的涡旋压缩机，其中，所述填充部从所述滑动主体部的端面一体地延伸，或者
    所述填充部以可拆卸的方式连接至所述滑动主体部。
  7. 根据权利要求6所述的涡旋压缩机，其中，在所述填充部以可拆卸的方式连接至所述滑动主体部的情况下，所述填充部通过螺纹紧固件连接至所述滑动主体部。
  8. 根据权利要求2所述的涡旋压缩机，其中，所述远端部段基本上沿所述定涡旋部件的径向方向延伸，并且所述远端部段具有在所述定涡旋部件的圆周方向上尺寸较大的长形形状。
  9. 根据权利要求2所述的涡旋压缩机，其中，所述旁通控制单元构造成选择性地向所述容置部段中引入高压流体或低压流体以在所述滑动件的相对两侧的压差下控制所述滑动件的运动。
  10. 根据权利要求9所述的涡旋压缩机，其中，所述旁通控制单元包括：
    控制阀(190)，所述控制阀具有第一端口、第二端口和第三端口，并且构造成在将所述第一端口连通至所述第三端口的第一位置与将所述第二端口连通至所述第三端口的第二位置之间切换；
    高压通道，所述高压通道将所述涡旋压缩机的高压区域连通至所述第一端口；
    低压通道，所述低压通道将所述涡旋压缩机的低压区域连通至所述第二端口；以及
    连通通道(193)，所述连通通道将所述容置部段连通至所述第三端口。
  11. 根据权利要求10所述的涡旋压缩机，其中，所述控制阀是电磁控制阀，并且所述控制阀安装至所述定涡旋部件。
  12. 根据权利要求10所述的涡旋压缩机，其中，所述定涡旋部件包括以可拆卸的方式连接的定涡旋主体部(150a)和盖板(150b)，所述高压通道、所述低压通道和所述连通通道均设置在所述盖板和/或所述定涡旋主体部中。
  13. 根据权利要求1至12中任一项所述的涡旋压缩机，其中，所述第一涡旋叶片具有关于所述动涡旋部件的中心轴线对称或不对称地布置的两个动涡旋叶片(162a、162b)，并且所述第二涡旋叶片具有关于所述定涡旋部件的中心轴线对称或不对称地布置的两个定涡旋叶片(152a、152b)。
  14. 根据权利要求1至12中任一项所述的涡旋压缩机，其中，所述涡旋压缩机还包括：
    至少一个调节通道，所述至少一个调节通道中的每个调节通道将所述多 个压缩腔中的一个压缩腔连通至所述涡旋压缩机的排气区域；以及
    至少一个单向阀，所述至少一个单向阀中的每个单向阀构造成仅允许相应的一个压缩腔中的工质在该相应的一个压缩腔中的压力大于预定压力时排出至所述排气区域。
  15. 根据权利要求1至12中任一项所述的涡旋压缩机，其中，所述偏置件为永磁体。
  16. 根据权利要求15所述的涡旋压缩机，其中，所述永磁体固定至所述涡旋压缩机的盖板中。
  17. 根据权利要求1至12中任一项所述的涡旋压缩机，其中，所述偏置件为弹性件。
  18. 根据权利要求17所述的涡旋压缩机，其中，所述滑动件具有与所述弹性件接合的凸缘，所述弹性件设置在所述滑动件的径向外侧。
PCT/CN2020/110165 2019-12-20 2020-08-20 涡旋压缩机 WO2021120656A1 (zh)

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