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WO2018151538A1 - Compresseur électrique - Google Patents

Compresseur électrique Download PDF

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Publication number
WO2018151538A1
WO2018151538A1 PCT/KR2018/001951 KR2018001951W WO2018151538A1 WO 2018151538 A1 WO2018151538 A1 WO 2018151538A1 KR 2018001951 W KR2018001951 W KR 2018001951W WO 2018151538 A1 WO2018151538 A1 WO 2018151538A1
Authority
WO
WIPO (PCT)
Prior art keywords
chamber
discharge chamber
rib
electric compressor
rear housing
Prior art date
Application number
PCT/KR2018/001951
Other languages
English (en)
Korean (ko)
Inventor
김홍민
정수철
임권수
임재훈
신인철
Original Assignee
한온시스템 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR1020170022412A external-priority patent/KR102530820B1/ko
Application filed by 한온시스템 주식회사 filed Critical 한온시스템 주식회사
Priority to CN201880002829.1A priority Critical patent/CN109477483B/zh
Priority to US16/314,566 priority patent/US11073316B2/en
Priority to DE112018000059.1T priority patent/DE112018000059B4/de
Priority to JP2019500564A priority patent/JP6742499B2/ja
Publication of WO2018151538A1 publication Critical patent/WO2018151538A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C29/06—Silencing
    • 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
    • F04C29/06—Silencing
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • 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
    • F04C29/06—Silencing
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/13—Noise

Definitions

  • the present invention relates to an electric compressor for minimizing vibration noise generated when a refrigerant chamber is discharged into the rear housing.
  • the compressor used in the air conditioning system sucks the evaporated refrigerant from the evaporator, converts it into a high temperature and high pressure state, which is easy to liquefy, and transfers the same to the condenser.
  • the compressor has a reciprocating type that performs the compression while the drive source for the compression to the refrigerant reciprocating and a rotary type that performs the compression while rotating, the reciprocating type to transfer the driving force of the drive source to the plurality of pistons using the crank
  • a crank type a swash plate type to be transmitted to a rotating shaft provided with a swash plate, and a wobble plate type using a wobble plate.
  • the rotary type there is a vane rotary type using a rotary rotary shaft and vanes, and a scroll type using a rotating scroll and a fixed scroll, and both the rotary, swash plate, and wobble plate types generate vibrations as high-pressure refrigerant is discharged into the discharge chamber. If the vibration is not attenuated for a certain time, pulsation due to vibration noise is caused in the rear housing having the discharge chamber.
  • the electric compressor is provided with a rear housing 10 in which a discharge chamber 11 through which refrigerant is discharged is formed. Since the rear housing 10 is made of a flat plate formed flat when viewed from the outside of the electric compressor, the volume of the discharge chamber 11 has a limited volume. In addition, the oil separator 20 is disposed obliquely on the rear housing 10 as shown in the drawing.
  • vibration noise is generated due to the tremor of the rear housing 10, which causes abnormal vibration of the vehicle or the air conditioning system equipped with the electric compressor. It acts as an inducing factor and needs countermeasures.
  • Embodiments of the present invention provide an electric compressor in which abnormal vibration and noise are minimized by increasing the internal volume of the discharge chamber of the rear housing so as to minimize vibration and noise caused by the discharge of the refrigerant in the electric compressor.
  • An electric compressor includes a rear housing 100 having a discharge chamber 110 through which a refrigerant is discharged; And an oil separator 200 disposed in the discharge chamber 110 and having a coolant inlet hole 202 for introducing the coolant therein, wherein the discharge chamber 110 has a volume outside the rear housing 100. Increased and protruded in multiple stages, characterized in that the interior of the discharge chamber 110 is divided into different volumes based on the oil separator 200.
  • the discharge chamber 110 may include a first chamber 112 partially protruding from the rear housing 100 in a protruding direction; A second chamber 114 partially protruding from the protruding end of the first chamber 112 at one side of the oil separator 200; And a third chamber 116 directly protruding in the protruding direction from the other side of the oil separator 200.
  • the second chamber 114 is larger in volume than the first chamber 112 or the third chamber 116.
  • the second chamber 114 protrudes longer in the protruding direction of the rear housing 100 than the length from which the first and third chambers 112 and 116 protrude.
  • the second chamber 114 is provided with a rib 300 extending in the circumferential direction of the rear housing 100 inside.
  • the rib 300 includes a first rib 310 formed in a ring shape in the second chamber 114;
  • the second rib 320 includes a plurality of second ribs 320 extending in a radial form from the first rib 310.
  • the second chamber 114 is provided with a third rib 330 divided into a plurality in the inner circumferential direction.
  • the first rib 310 and the second rib 320 may be formed in different thicknesses.
  • the first rib 310 is thicker than the second rib 320.
  • the oil separator 200 is characterized in that it is disposed eccentrically on one side with respect to the center of the rear housing (100).
  • the partition 400 for partitioning the interior of the discharge chamber 110 into different areas.
  • the partition 400 is characterized in that the communication portion 410 is formed in different positions.
  • the discharge chamber 110 is a volume ratio of the discharge chamber is set according to the internal volume (V1) of a predetermined size and the refrigerant discharge capacity (cc) of the refrigerant discharged to the discharge chamber 110, the discharge chamber (
  • the volume ratio of 110 is calculated by dividing the internal volume V1 of the discharge chamber 110 by the refrigerant discharge capacity cc, and the volume ratio of the discharge chamber 110 is any one of 2.0 to 3.2 times. Characterized in that the ratio of.
  • the discharge chamber 110 may include a first region S1 having a largest region among a plurality of regions located at different positions by the oil separator 200; A second region S2 having a region relatively smaller than the first region S1; And a third region S3 adjacent to the refrigerant inlet hole 202 and located adjacent to the second region S2.
  • the first region S1 is formed in the shape of a semi-circle, and the refrigerant discharged into the first region S1 diffuses inside the first region S1 or moves along the circumferential direction to reduce noise. It features.
  • the discharge chamber 110 is characterized in that the rib 300 is formed on one side adjacent to the oil separator 200, the rib 300 is not formed on the other side of the oil separator 300.
  • the electric compressor according to the present embodiment is mounted in a vehicle air conditioning system.
  • Embodiments of the present invention can minimize the vibration and noise caused by the discharge of the refrigerant which is the operating medium of the electric compressor, and can prevent the problem caused by the pulsating pressure to achieve a quiet operation of the installation object is installed. .
  • Embodiments of the present invention can improve the overall structural strength of the rear housing by changing the structure to achieve the volume increase and rigidity reinforcement of the discharge chamber at the same time.
  • FIG. 1 is a view showing a rear housing provided in a conventional electric compressor.
  • FIG. 2 is a cross-sectional view showing an electric compressor according to an embodiment of the present invention.
  • FIG 3 is a side view showing a rear housing of the electric compressor according to an embodiment of the present invention.
  • FIG. 4 is a view showing the inside of the rear housing of the electric compressor according to an embodiment of the present invention.
  • FIG. 5 is a view showing a third rib provided in the rear housing of the electric compressor according to another embodiment of the present invention.
  • FIG. 6 is a side view illustrating various embodiments of a discharge chamber formed in the rear housing.
  • FIG. 7 is a graph showing the noise reduction effect according to the volume ratio of the discharge chamber according to an embodiment of the present invention.
  • FIG. 8 is a graph showing the weight according to the volume ratio of the discharge chamber according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view showing a motor-driven compressor according to an embodiment of the present invention
  • Figure 3 is a view showing a rear housing of the motor-driven compressor according to an embodiment of the present invention
  • Figure 4 is a view of the present invention The figure shows the inside of the rear housing of the electric compressor according to the embodiment.
  • the motor-driven compressor 1 performs oil separation of oil contained in a coolant and vibrates in the rear housing 100 by discharge of the coolant. Or to minimize the occurrence of noise to increase the internal volume of the discharge chamber 110 to prevent problems caused by vibration.
  • the present invention is limited to use in a vehicle air conditioning system equipped with a motor-driven compressor, it turns out that it can be applied to industrial compression unit or home air conditioning system.
  • Electric compressor (1) is formed of a front housing (2a) and the intermediate housing (2b) and the rear housing (100) formed in the inlet position where the refrigerant is sucked to form an outer shape
  • the intermediate housing (2b) has a drive unit (inside) 3) and a compression unit 5 are built in
  • the drive part 3 comprises a stator, a rotor, and a rotating shaft 4 inserted in the center of the rotor.
  • the rotational force generated by the motor unit 3 is transmitted to the compression unit 5 to compress and discharge the refrigerant.
  • the compression unit 5 includes a fixed scroll and a swing scroll.
  • the fixed scroll is maintained in a fixed state in the electric compressor (1), the pivoting scroll is installed so as to be eccentrically rotatable with respect to the fixed scroll to compress the refrigerant while the relative movement is made.
  • the rear housing 100 is located at one end of the intermediate housing 2b. More specifically, the rear housing 100 is selectively detachably mounted to the intermediate housing 2b while being in close contact with the right end with reference to the drawings.
  • the refrigerant discharged from the unit 5 is discharged at a predetermined pressure toward the discharge chamber 110 through the discharge hole via the back pressure chamber. And the pressure of the refrigerant discharged to the discharge chamber 110 is discharged at a pressure of about 30bar or so may generate noise.
  • Electric compressor 1 is a rear housing 100 is formed with a discharge chamber 110 for discharging the refrigerant, and the refrigerant inlet hole disposed in the discharge chamber 110 and the refrigerant flows ( 202 is formed, the oil separator 200 is formed, the discharge chamber 110 is increased in volume to the outside of the rear housing 100 protrudes in multiple stages, the discharge chamber based on the oil separator 200 The interior of 110 is divided into different volumes.
  • the discharge chamber 110 may include a first chamber 112 partially protruding from the rear housing 100 in a protruding direction from the rear housing 100 and the first chamber 112 at one side of the oil separator 200.
  • the second chamber 114 partially protrudes from the protruding end of the) and the third chamber 116 protrudes directly in the protruding direction from the other side of the oil separator 200.
  • the first to third chambers 112, 114, and 116 all induce noise reduction through volume increase when the refrigerant is discharged.
  • the first to third chambers 112, 114, and 116 do not have a limited volume and have a discharge chamber 110 having a specific ratio. To reduce the vibration noise caused by the refrigerant discharge.
  • the first chamber 112 is positioned adjacent to the second chamber 114 and is formed in a predetermined size on one side with respect to the center of the discharge chamber 110.
  • the first chamber 112 may protrude in a crescent form to the outside of the rear housing 100.
  • the discharge chamber 110 Since the discharge chamber 110 is subjected to an impact corresponding to the aforementioned pressure range when the refrigerant is discharged, noise may be reduced due to a diffusion effect when the volume of the discharge chamber 110 is increased.
  • the second chamber 114 is located at the center of the discharge chamber 110 adjacent to the first chamber 112, for example, is located at one side of the oil separator 200.
  • the second chamber 114 has a volume larger than that of the first chamber 112 or the third chamber 116.
  • the second chamber 114 has the largest volume since the refrigerant is discharged at a position not seen with the second chamber 114. It consists of.
  • the second chamber 114 When the refrigerant is discharged to the discharge chamber 110, the second chamber 114 may be formed in the above-described position because the second chamber 114 may diffuse in a radial form at an opposite position to induce a noise and vibration reduction effect more advantageously.
  • the layout of the rear housing 110 can be improved without complicating the layout of the rear housing 110, so that the noise attenuation effect can be improved.
  • the second chamber 114 has a larger volume than the first chamber 112, the space for diffusion can be stably maintained when the refrigerant is discharged, thereby improving the noise attenuation effect.
  • the second chamber 114 is maintained in an arrangement form partially surrounded by the first chamber 112 in the circumferential direction.
  • the pressure fluctuation due to the discharge of the refrigerant is primarily diffused in the first chamber 112 and then further diffused in the second chamber 114, which is advantageous in reducing vibration and noise.
  • the second chamber 114 protrudes longer in the protruding direction of the rear housing 100 than the protruding lengths of the first and third chambers 112 and 116.
  • the second chamber 114 has a protruding length protruding in a specific length range and varies according to the specifications of the electric compressor.
  • the third chamber 116 is located on the other side of the oil separator 200 on the basis of the drawing and is composed of a smaller volume than the first and second chambers 112 and 114.
  • the third chamber 116 is positioned at the edge of the rear housing 100 to reduce noise due to the discharge of the refrigerant in consideration of the limited layout of the rear housing 100, and the shape is not limited to the shape shown in the drawings. .
  • the rear housing 100 has ribs 300 extending in the circumferential direction of the rear housing 100 inside the second chamber 114 to minimize vibration caused by the discharge pressure of the refrigerant discharged from the discharge chamber 110. ) Is provided.
  • the rib 300 may be formed at the position to suppress or support vibration or noise generated by the discharge of the refrigerant, thereby achieving rigid reinforcement.
  • the rib 300 includes a first rib 310 formed in a ring shape in the second chamber 114, and a plurality of second ribs 320 extending radially from the first rib 310. .
  • the first rib 310 is formed in a ring shape, when vibration is transmitted to the first rib 310, the vibration of the rear housing 100 is partially transmitted to the second rib 320, which will be described later. Vibration may be diffused in the direction so that the overall vibration in the rear housing 100 is attenuated.
  • the first rib 310 is located at a lower position than the refrigerant inlet hole 202.
  • the second rib 320 is positioned at a position spaced apart from the refrigerant inlet hole 202 to prevent vibration from being transmitted to the refrigerant inlet hole 202, thereby promoting stable movement of the refrigerant gas.
  • vibration and noise generated in the second chamber 114 occupying most of the area of the rear housing 100 may be minimized.
  • the first rib 310 and the second rib 320 according to the present embodiment may have different thicknesses or the same thickness.
  • the time and attenuation amount of the vibration are transmitted may vary depending on the position, so the exact thickness may be changed according to the capacity of the electric compressor through a plurality of experiments.
  • first and second ribs 310 and 320 may be changed to the shapes shown in the drawings or other shapes.
  • the cross section is in the form of either a semi-circle or an ellipse or a polygonal shape.
  • the angles formed between the two ribs 320 may be maintained at a constant level. If the second ribs 320 are different from each other, the second ribs 320 may have different angles.
  • the second chambers 114 are divided into the same area by the second ribs 320 to discharge the refrigerant. It may be most advantageous for reducing vibrations.
  • the length of the second rib 320 extending to the place where the oil separator 200 is located is extended to the second rib extending to another place.
  • the area partitioned by the second rib 320 extending to the oil separator 200 may be configured to have a smaller area than other places.
  • the first rib 310 may be thicker than the second rib 320, and the final thickness is set through a plurality of experiments to reinforce the strength of the second chamber 114.
  • the first rib 310 may be thick or thin at a specific position according to the degree of vibration generated after the refrigerant is discharged toward the rear housing 100.
  • the second rib 320 may also be formed to have a thick thickness at a location where a lot of vibration is generated and to be thin at a location where a vibration is relatively low. Accordingly, the occurrence of vibration may be minimized by changing the thickness of the second rib 320 at a location where a lot of vibration is generated for each position of the rear housing 100.
  • the fourth rib 340 extends from the first rib 310 toward the oil separator 200.
  • the fourth rib 340 may extend to the length shown in the drawing due to the layout of the rear housing 100, but may also be extended to an increased length.
  • the fourth rib 340 is located below the refrigerant inlet hole 202.
  • a separate obstacle is disposed in the moving path, so that the refrigerant is positioned below the refrigerant inlet hole 202 on the basis of the drawing.
  • the discharge chamber 110 has the rib 300 formed at one side adjacent to the oil separator 200, and the rib 300 is not formed at the other side of the oil separator 300.
  • the rib 300 is arranged as above in consideration of the layout and space limitations of the rear housing 100 to reinforce structural rigidity.
  • the second chamber 114 is provided with a plurality of third ribs 330 divided along the inner circumferential direction.
  • the third rib 330 is disposed in the form shown in the figure for rigid reinforcement at the center position of the rear housing 100.
  • the plurality of third ribs 330 may be divided at regular intervals, and the shape may be variously changed in addition to the shape shown in the drawings.
  • the rear housing 100 is formed in a disc shape, and a plurality of mounting holes for bolting coupling are formed in the circumferential direction to be mounted on the intermediate housing 2b, and the discharge chamber 110 is formed in a separate area therein.
  • the sealing process is performed to prevent external leakage of the refrigerant through a sealing member (not shown), even when a high-pressure refrigerant is discharged into the discharge chamber 110, leakage does not occur.
  • the rear housing 100 includes an oil separator 200 disposed in the discharge chamber 110 and having a refrigerant inlet hole 202 for introducing the refrigerant moved into the discharge chamber 110. It is limited to being disposed in an eccentric state on one side of the rear housing 100 and shown as having two refrigerant inlet holes formed in the upper middle on the basis of the longitudinal direction of the oil separator 200, but the number can be changed. .
  • the oil separator 200 is limited to be inclined to the rear housing 100, and is formed in the rear housing 100 in a state of protruding toward the inner side of the discharge chamber 110 partitioned by the sealing member.
  • the oil separator 200 may be formed in a hollow state, and the oil contained in the refrigerant introduced into the refrigerant inlet hole 202 may move to a lower side of the oil separator 200 due to the difference in specific gravity. The refrigerant is moved through the inner upper portion of the oil separator 200.
  • the partition wall 400 partitions an inner region of the discharge chamber 110 via the oil separator 200, and the movement time of the refrigerant flowing into the refrigerant inlet hole 202 is different from each other.
  • the communicating part 410 is formed in another position.
  • a communication part 410 is formed in the partition wall 400, and refrigerant flows through the communication part 410 due to different inflow times of the refrigerant flowing into the communication part 410 from the discharge chamber 110. Phase difference occurs and pulsation noise is reduced.
  • the refrigerant inlet hole 202 is located on the upper side of the oil separator 200 based on the length direction. It is preferably located at.
  • the partition wall 400 is processed in the form shown in the drawings through a cutting method and the communication unit 410 is manufactured through additional processing after the hole processing is primarily made through a drill.
  • the electric compressor (1) is provided with a filter unit 30 for filtering the separated oil via the oil separator 200, the filter unit 30 is foreign matter contained in the oil separated through the oil separator (200) It is provided to filter the filter unit 30 is configured to include a filter frame seated on the filter body consisting of a mesh form.
  • the filter unit 30 is oil separated from the refrigerant before the oil discharged through the oil discharge hole (not shown) formed at the lower side of the oil separator 200 is supplied to the drive unit 3 of the electric compressor 1.
  • the installation position in the discharge chamber 110 is changed according to the position of the oil separator 200 for filtering on.
  • the filter unit 30 also corresponds to one side of the oil separator 200 as shown in the drawing. Is located on the right side.
  • the electric compressor 1 according to the present embodiment is mounted in a vehicle air conditioning system, vibration and noise transmission are minimized to the interior of the vehicle, thereby maintaining quiet operation.
  • the discharge chamber 110 includes a first region S1 having the largest region among a plurality of regions located at different positions by the oil separator 200, and a region relatively smaller than the first region S1. And a third region S3 adjacent to the refrigerant inlet hole 202 and located adjacent to the second region S2.
  • the first to third regions S1 to S3 are maintained in the same region, but are divided into regions shown in the drawing based on the oil separator 200, and noise attenuation is mainly performed in the first and second regions S1 and S2. Can be done.
  • the third region S3 may reduce noise generated while the refrigerant is introduced into the refrigerant inlet hole 202, but assists noise reduction with the first and second regions S1 and S2. It can also be done.
  • the first region S1 may be formed in a semi-circle shape, and noise may be attenuated while the refrigerant discharged to the first region S1 diffuses inside the first region S1 or moves along the circumferential direction. have.
  • the discharge chamber 110 is discharged according to an internal volume V1 having a predetermined size and a refrigerant discharge capacity cc in which refrigerant is discharged to the discharge chamber 110.
  • the volume ratio of the chamber is set.
  • the volume ratio of the discharge chamber 110 is calculated by dividing the internal volume V1 of the discharge chamber 110 by the refrigerant discharge capacity cc, and the volume ratio of the discharge chamber 110 is 2.0. It consists of any one of ⁇ 3.2 times.
  • the rear housing provided in the electric compressor may be composed of a plurality of types from the A type to the E type, and the rear housing 100 shown in the A type corresponds to a form in which the discharge amount is almost absent.
  • the rear housing 100 shown in the B type is provided in the discharge chamber 110 and the discharge length is derived to a length corresponding to e1.
  • the rear housing 100 shown in type C has a discharge chamber 110 with a length corresponding to e2
  • the rear housing 100 shown in a D type has a discharge chamber 110 with a length corresponding to e3.
  • the discharge chamber 110 is drawn to a length corresponding to e4.
  • the rear housing 100 shown in Types A to E all have different internal volumes and refrigerant discharge capacities.
  • the discharge capacities of the refrigerants are all constant, but the internal volumes of the rear housing 100 are different from each other. do.
  • the smallest internal volume of the rear housing 100 of the A type is maintained at 61 cc, and the largest internal volume of the rear housing 100 of the D type is maintained at 117 cc.
  • the weight of the rear housing according to the A to E type is different from each other, the weight of the A-type rear housing 100 is maintained at the lowest 462g, the weight of the D type rear housing 100 is the largest The weight is maintained.
  • the discharge chamber 110 is composed of any one of the ratio of the volume of the discharge tamper 110 is 2.0 to 3.2 times the length derived to the outside of the rear housing 100, the maximum according to each different ratio
  • the rear housing can be designed in which noise reduction performance is maintained.
  • the rear housing 100 may generate excessive noise when the volume ratio of the discharge chamber 110 is less than 2.0 times, and when the volume ratio exceeds 3.2 times, the rear housing 100 may use the rear housing 9100 in which the above volume ratio is maintained. It can be seen that it is most preferable to do.
  • the discharge chamber 110 is discharged according to an internal volume V1 having a predetermined size and a refrigerant discharge capacity cc in which refrigerant is discharged to the discharge chamber 110.
  • the volume ratio of the chamber is set.
  • the noise shown in the Y-axis relative to the refrigerant discharge capacity shown in the X-axis is the noise generated in the rear housing at the 3.1 times the position is most reduced.
  • the rear housing corresponding to the ratio of 3.0 to 3.15 has an excellent noise reduction effect due to the discharge of the refrigerant.
  • the noise is increased when the volume ratio of the discharge chamber 110 is 3.15 times or 3.2 times or more, it can be seen that it is most preferable to use the rear housing in which the above-described volume ratio is maintained.
  • the discharge chamber 110 protrudes in a range of at least 14 mm and at most 30 mm, the length of which protrudes to the outside of the rear housing 100, and the noise reduction effect due to the discharge of the refrigerant within the above range is most reduced. do.
  • the present embodiments can be used to reduce the vibration and noise generated by the discharge of the refrigerant in the electric compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

La présente invention concerne un compresseur électrique. Selon un mode de réalisation, la présente invention concerne un compresseur électrique comprenant : un boîtier arrière (100) dans lequel est formée une chambre de décharge (110) destinée à décharger un fluide frigorigène; et un séparateur d'huile (200) disposé dans la chambre de décharge (110) et comprenant un trou d'entrée de fluide frigorigène (202) dans lequel le fluide frigorigène est introduit, la chambre de décharge (110) augmentant en volume vers l'extérieur du boîtier arrière (100) pour en faire saillie en plusieurs étapes, et l'intérieur de la chambre de décharge (110) est divisé en différents volumes par rapport au séparateur d'huile (200).
PCT/KR2018/001951 2016-11-30 2018-02-14 Compresseur électrique WO2018151538A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN201880002829.1A CN109477483B (zh) 2016-11-30 2018-02-14 电动压缩机
US16/314,566 US11073316B2 (en) 2016-11-30 2018-02-14 Electric compressor
DE112018000059.1T DE112018000059B4 (de) 2016-11-30 2018-02-14 Elektrischer Kompressor
JP2019500564A JP6742499B2 (ja) 2016-11-30 2018-02-14 電動圧縮機

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
KR20160161105 2016-11-30
KR10-2017-0022412 2017-02-20
KR1020170022412A KR102530820B1 (ko) 2016-11-30 2017-02-20 전동압축기

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WO2018151538A1 true WO2018151538A1 (fr) 2018-08-23

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DE (1) DE112018000059B4 (fr)
WO (1) WO2018151538A1 (fr)

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KR102730508B1 (ko) * 2019-08-22 2024-11-13 현대자동차주식회사 다단 압축 장치 및 그의 제어방법
JP6985625B2 (ja) 2020-03-31 2021-12-22 ダイキン工業株式会社 油分離器

Citations (5)

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JP2778585B2 (ja) * 1996-06-14 1998-07-23 松下電器産業株式会社 スクロール気体圧縮機
KR20100103139A (ko) * 2009-03-13 2010-09-27 한국델파이주식회사 스크롤 압축기
KR20140127081A (ko) * 2013-04-24 2014-11-03 엘지전자 주식회사 압축기용 머플러 및 이를 구비한 압축기
KR20160108036A (ko) * 2015-03-06 2016-09-19 한온시스템 주식회사 전동압축기
KR101681590B1 (ko) * 2015-09-09 2016-12-01 엘지전자 주식회사 스크롤 압축기

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JP5594196B2 (ja) * 2011-03-14 2014-09-24 株式会社豊田自動織機 車両用スクロール型圧縮機
KR102080621B1 (ko) * 2015-03-06 2020-04-14 한온시스템 주식회사 전동압축기 및 상기 전동압축기의 유분리기 가공 방법
KR102379705B1 (ko) 2015-08-20 2022-03-28 삼성전자주식회사 그라운드 스위치를 갖는 메모리 장치
CN106286294B (zh) * 2016-09-19 2019-06-07 珠海格力电器股份有限公司 涡旋压缩机

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2778585B2 (ja) * 1996-06-14 1998-07-23 松下電器産業株式会社 スクロール気体圧縮機
KR20100103139A (ko) * 2009-03-13 2010-09-27 한국델파이주식회사 스크롤 압축기
KR20140127081A (ko) * 2013-04-24 2014-11-03 엘지전자 주식회사 압축기용 머플러 및 이를 구비한 압축기
KR20160108036A (ko) * 2015-03-06 2016-09-19 한온시스템 주식회사 전동압축기
KR101681590B1 (ko) * 2015-09-09 2016-12-01 엘지전자 주식회사 스크롤 압축기

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CN109477483A (zh) 2019-03-15
JP2019520520A (ja) 2019-07-18
DE112018000059T5 (de) 2019-03-07
JP6742499B2 (ja) 2020-08-19
DE112018000059B4 (de) 2025-05-08
CN109477483B (zh) 2020-05-15

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