Electric compressor with bearing oil communication hole

Abstract

An electric compressor includes a housing, a refrigerant inlet port, a refrigerant outlet port, an inverter section, a motor section, a compression device, and a front cover. The housing defines an intake volume and an exhaust volume. A refrigerant inlet port is coupled to the housing and configured to introduce refrigerant to the intake volume. The compression device is a scroll compression device configured to be capable of compressing a refrigerant. A refrigerant outlet port is coupled to the housing and configured to allow compressed refrigerant to exit the scroll electric compressor from the exhaust volume.

Description

Technical Field

[0001] The present invention generally relates to an electric compressor, and more particularly to an electric compressor that compresses refrigerant using a scroll compression device. Background Art

[0002] Compressors have long been used in cooling systems. In particular, scroll compressors, in which an orbiting scroll rotates in a circular motion relative to a fixed scroll to compress a refrigerant, have been used in systems designed to provide cooling in a specific area. For example, such scroll compressors have long been used in HVAC systems of motor vehicles such as automobiles to provide air conditioning. Such compressors can also be used in turn in applications requiring heat pumps. Typically, these compressors are driven using the rotational motion from the automobile engine.

[0003] With the advent of battery-powered or electric vehicles and / or hybrid vehicles where the vehicle may sometimes be powered only by the battery, such compressors must be driven or powered by the battery rather than the engine. Such compressors may be referred to as electric compressors.

[0004] In addition to cooling the passenger compartment of a motor vehicle, an electric compressor may be used to provide heating or cooling to other areas or components of a motor vehicle. For example, it may be desirable to heat or cool the electronic systems and the battery or battery compartment while the battery is being charged, particularly during a fast charge mode, as the heat generated at this time may damage or degrade the battery and / or other systems. It may also be used to cool the battery during times when the battery is not being charged or in use, as the heat may damage or degrade the battery. Since the electric compressor may be operating at various times, even when the motor vehicle is not operating, such use obviously requires electrical energy from the battery, thereby reducing the operating time of the battery.

[0005] In addition, electric compressors can run at very high speeds, for example, 2000 RPM (or more). Such high speeds may generate undesirable noise levels.

[0006] Therefore, it is desirable to provide an electric compressor with high efficiency, low noise and maximum operating life.The present invention is directed to solving one or more of the above problems or advantages. Summary of the invention

[0007] In a first embodiment of the present invention, a scroll electric compressor configured to compress refrigerant is provided. The scroll electric compressor includes a housing, a first ball bearing, a second ball bearing, a refrigerant inlet port, a refrigerant outlet port, an inverter module, a motor, a drive shaft and a compression device. The housing defines an intake volume and an exhaust volume and includes a first drive shaft support member and a second drive shaft support member. The first ball bearing is located in the first drive shaft support member. The first drive shaft support member of the housing includes an oil communication hole for allowing oil to enter the first ball bearing. The second ball bearing is located in the second drive shaft support member. The refrigerant inlet port is connected to the housing and is configured to introduce refrigerant into the intake volume. The refrigerant outlet port is connected to the housing and is configured to allow compressed refrigerant to leave the scroll electric compressor from the exhaust volume. The inverter module is installed in the housing and is suitable for converting direct current into alternating current. The motor is installed in the housing. The drive shaft is connected to the motor. The drive shaft has a first end and a second end. The first end of the drive shaft is positioned in the first bearing, and the second end of the drive shaft is positioned in the second bearing. The compression device receives refrigerant from the intake volume and compresses the refrigerant as the drive shaft is rotated by the motor.

[0008] In a second embodiment of the present invention, a scroll electric compressor having a central axis and configured to compress refrigerant is provided. The scroll electric compressor includes a housing, a refrigerant inlet port, a refrigerant outlet port, an inverter section, a motor section, and a compression device. The housing defines an intake volume and an exhaust volume. The refrigerant inlet port is coupled to the housing and is configured to introduce refrigerant into the intake volume. The refrigerant outlet port is coupled to the housing and is configured to allow compressed refrigerant to leave the scroll electric compressor from the exhaust volume.

[0009] The inverter section includes an inverter housing, an inverter back cover and an inverter module. The inverter housing includes a first drive shaft support member. The inverter back cover is connected to the inverter housing and forms an inverter cavity. The inverter module is installed in the inverter cavity and is used to convert direct current into alternating current.

[0010] The motor section includes a motor housing, a drive shaft, a first ball bearing, a second ball bearing and a motor. The motor housing forms a motor cavity and is mounted to the inverter housing. The motor housing has a second drive shaft support member. The drive shaft is located in the motor housing, has a first end and a second end and defines a central axis. The first ball bearing is located in the first drive shaft support member. The first drive shaft support member of the housing has an oil communication hole for allowing oil to enter the first ball bearing. The second ball bearing is located in the first drive shaft support member. The motor is located in the motor housing and is configured to controllably rotate the drive shaft around the central axis. The compression device receives refrigerant from the intake volume and compresses the refrigerant as the drive shaft is rotated by the motor. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] These and other features and advantages of the present invention will become more readily understood when considered in conjunction with the following detailed description and accompanying drawings.

[0012] Figure 1 is a first perspective view of a motor-driven compressor according to an embodiment of the present invention.

[0013] Figure 2 yes Figure 1 A second perspective view of the electric compressor.

[0014] Figure 3A The inverter back cover of the inverter section is shown. Figure 1 A first side view of an electric compressor.

[0015] Figure 3B yes Figure 3A A perspective view of the inverter rear cover.

[0016] Figure 3C is a first perspective view of an inverter back cover according to an alternative embodiment of the present invention.

[0017] Figure 3D yes Figure 3C Second perspective view of the inverter back cover.

[0018] Figure 4 yes Figure 1 A second side view of the electric compressor.

[0019] Figure 5 yes Figure 1 Front view of an electric compressor.

[0020] Figure 6 yes Figure 1 Rear view of the electric compressor.

[0021] Figure 7 yes Figure 1 A top view of an electric compressor.

[0022] Figure 8 yes Figure 1 Bottom view of the electric compressor.

[0023] Fig. 9 yes Figure 1 A first cross-sectional view of an electric compressor.

[0024] Fig.10 yes Figure 1 A second cross-sectional view of the electric compressor.

[0025] Fig.11 yes Figure 1 Exploded view of the inverter of the electric compressor.

[0026] Fig.12 yes Figure 1 An exploded view of the portion of the electric compressor including the motor and drive shaft.

[0027] Fig.13 yes Figure 1 Exploded view of the compression device of an electric compressor.

[0028] Fig.14A yes Fig.12 A first perspective view of the drive shaft.

[0029] Fig. 14B yes Fig.14A A second perspective view of the drive shaft.

[0030] Fig.15A yes Fig.12 A first perspective view of the rotor and counterweight of the motor.

[0031] Fig. 15B yes Fig.15A A second perspective view of the rotor and counterweight.

[0032] Fig.16A yes Figure 1 A first perspective view of a portion of an electric compressor including an orbiting scroll, a drive pin and a swing link mechanism.

[0033] Fig. 16B yes Fig.16A A second perspective view of a portion of an electric compressor.

[0034] Fig. 16C yes Fig.13 A perspective view of the plug of a compression device.

[0035] Fig.16D yes Fig. 16C A second perspective view of the stopper.

[0036] Fig.16E yes Fig. 16C A cross-sectional view of the plug.

[0037] Fig.16F yes Fig.11 A perspective view of an inverter housing of an inverter.

[0038] Figure 16G yes Fig.13 A partial enlarged view of the compression device.

[0039] Figures 17A-17J According to an embodiment of the present invention Figure 1 A graphical representation of the fixed scroll and orbiting scroll of the compression device of an electric compressor.

[0040] Fig.18A yes Fig.13 A first perspective view of a portion of a compression device including a fixed scroll and an orbiting scroll.

[0041] Fig.18B yes Fig.18A A second perspective view of a portion of a compression device.

[0042] Fig.18C yes Fig.13 A first perspective view of a fixed scroll of a compression device.

[0043] Fig.18D yes Fig.13 A second perspective view of the fixed scroll of the compression device.

[0044] Fig.18E yes Fig.13 A third perspective view of the fixed scroll of the compression device.

[0045] Fig.18F is with Fig.13 A perspective view of the reed mechanism associated with the compression device.

[0046] Fig.19A is a first perspective view of a front cover of an electric compressor forming an oil separator according to one embodiment of the present invention.

[0047] Fig.19B yes Fig.19A A second perspective view of the front cover of FIG.

[0048] Fig. 20 is a first perspective view of a front cover of a motor-driven compressor forming an oil separator according to a second embodiment of the present invention. DETAILED DESCRIPTION

[0049] Referring to the accompanying drawings, in which the same reference numerals in multiple views represent the same or corresponding parts, an electric compressor 10 having an outer housing 12 is provided. The electric compressor 10 is particularly suitable for use in motor vehicles, such as automobiles (not shown). The electric compressor 10 can be used as a cooling device or as a heat pump (conversely) to heat and / or cool different aspects of the vehicle. For example, the electric compressor 10 can be used as part of a heating, ventilation and air conditioning (HVAC) system in an electric vehicle (not shown) to cool or heat the passenger compartment. In addition, the electric compressor 10 can be used to heat or cool the passenger compartment, onboard electronic equipment and / or for batteries that power the vehicle when the vehicle is not operating, for example, during a charging cycle. The electric compressor 10 can also be used when the vehicle is not operating and the battery is not charging to maintain battery life or minimize degradation of battery life. In the illustrated embodiment, the electric compressor 10 has a displacement of 57 cubic centimeters (cc). Displacement refers to the initial volume captured in the compression device when the scroll disk of the compression device is initially closed or contacted (see below). It should be noted that the motor-compressor 10 disclosed herein is not limited to any such capacity, and may be sized or proportioned to meet particular desired specifications.

[0050] In the illustrated embodiment, the electric compressor 10 is a scroll compressor for quickly and efficiently compressing refrigerant for use in various systems of a motor vehicle, such as an electric or hybrid vehicle. The electric compressor 10 may use a mixture of refrigerant and oil, which may be simply referred to as "refrigerant," throughout its operation.

[0051] The electric compressor 10 includes an inverter section 14, a motor section 16, and a compression device (or compression assembly) 18 contained within an outer housing 12. The outer housing 12 includes an inverter back cover 20, an inverter housing 22, a motor housing 24, a fixed scroll 26, and a front cover 28 (which may be referred to as a discharge header).

[0052] In a first aspect of the electric compressor 10 of the present disclosure, there is provided an electric compressor 10 having a swing link mechanism and a drive shaft with an integrated limiting pin. In a second aspect of the electric compressor 10 of the present disclosure, there is provided an electric compressor 10 having an oil separator. In a third aspect of the electric compressor 10 of the present disclosure, there is provided an electric compressor 10 having a vortex bearing oil injection. In a fourth aspect of the electric compressor of the present disclosure, there is provided an electric compressor 10 having a bearing oil connecting hole. In a fifth aspect of the present invention, there is provided an electric compressor 10 having a dome-shaped inverter cover.

[0053] In one embodiment, the inverter back cover 20, inverter housing 22, motor housing 24, fixed scroll 26, and front cover 28 are constructed of machined aluminum. The inverter 10 may be mounted via a plurality of mounting points 120, for example, within the body of a motor vehicle.

[0054] General Arrangement and Operation of the Electric Compressor 10

[0055] The inverter back cover 20 and the inverter housing 22 form an inverter cavity 30. The inverter back cover 20 is mounted to the inverter housing 22 by a plurality of bolts 32. The inverter back cover 20 and the inverter housing 22 are mounted to the motor housing 24 by a plurality of bolts 34, which extend through holes 36 in the inverter back cover 20 and holes 38 in the inverter housing 22 and are threaded into threaded holes 40 in the motor housing 24. An inverter gasket 42 positioned between the inverter back cover 20 and the inverter housing 22 prevents moisture, dust, and other contaminants from entering the internal cavity 30. A motor gasket 54A is positioned between the inverter housing 22 and the motor housing 24 to prevent moisture, dust, and other contaminants from entering the motor housing 24.

[0056] refer to Fig.11 , the inverter module 44 is mounted in the inverter cavity 30 formed by the inverter back cover 20 and the inverter housing 22. The inverter module 44 includes an inverter circuit 46 mounted on a printed circuit board 48, and the printed circuit board 48 is mounted on the inverter housing 22. The inverter circuit 46 converts the direct current (DC) received from the outside of the electric compressor 10 into a three-phase alternating current (AC) to supply / drive the motor 54 (see below). The inverter circuit 46 also controls the speed of the electric compressor 10. The high voltage DC current is supplied to the inverter circuit 46 via the high voltage connector 50. The low voltage DC current for driving the inverter circuit 46 and the control signal for controlling the operation of the inverter circuit 46 and the motor section 16 are supplied via the low voltage connector 52.

[0057] The motor section 16 includes a motor 54 located within a motor cavity 56. The motor cavity 56 is formed by the motor side 22A of the inverter housing 22 and the interior surface 24A of the motor housing 22. Fig.12 , the motor 54 is a three-phase AC motor having a stator 56. The stator 56 has a generally hollow cylindrical shape with six individual coils (two per phase). The stator 56 is contained within and mounted to the motor housing 22 and remains stationary relative to the motor housing 22.

[0058] The motor 54 includes a rotor 60 located within and centered relative to the stator 58. The rotor 60 has a generally hollow cylindrical shape and is located within the stator 56. The rotor 60 has a plurality of balancing weights 60A, 60B fixed thereto. The balancing weights balance the motor 54 when the motor 54 drives the compression device 18, and the balancing weights may be machined from brass.

[0059] Power is supplied to the motor 54 via a set of terminals 54A which are sealed to the motor cavity 56 by O-rings 54B.

[0060] The drive shaft 90 is coupled to the rotor 60 and rotates with it. In the illustrated embodiment, the drive shaft 90 is press-fitted in the center hole 60C of the rotor 60. The drive shaft 90 has a first end 90A and a second end 90B. The inverter housing 22 includes a first drive shaft support member 22B located on the motor side of the inverter housing 22. The first ball bearing 62 located in the hole formed by the first drive shaft support member 22 supports the first end of the drive shaft 90 and allows the first end of the drive shaft 90 to rotate. The motor housing 24 includes a second drive shaft support member 24A. The second ball bearing 64 located in the hole formed by the second drive shaft support member 24A allows the second end 90B of the drive shaft 90 to rotate. In the illustrated embodiment, the first ball bearing 62 and the second ball bearing 64 are press-fitted with the holes formed by the first drive shaft support member 22 of the inverter housing 22 and the second drive shaft support member 24A of the motor housing 24, respectively.

[0061] As described above, the electric compressor 10 is a scroll compressor. The compression device 18 includes the fixed scroll 26 and the orbiting scroll 66. The orbiting scroll 66 is fixed to the second end of the rotor 60B. The rotor 60 and the orbiting scroll 66 rotate under the control of the inverter module 44.

[0062] refer to Fig.14A , Fig. 14B , Fig.16A and Fig. 16B The drive shaft 90 has a central axis 90C about which the rotor 60 and the drive shaft 90 rotate. The orbiting scroll 66 rotates in an eccentric orbit about the central axis 90C, i.e., moves in a circular motion, while the orientation of the orbiting scroll 66 remains unchanged relative to the fixed scroll 26. The center of the orbiting scroll 66 is along an orbiting scroll hole 90E (see FIG. 1 ) located at the second end 90D of the drive shaft 90. Fig.14A ) is positioned about the offset axis 90D of the drive shaft 90 defined by the motor 54. When the drive shaft 90 is rotated by the motor 54, the center of the orbiting scroll 66 follows the movement of the orbiting scroll hole 90E as the drive shaft 90 rotates about the central axis 60C.

[0063] As used below, specific references Figure 1 , Figure 2 and Fig. 9 , the mixed refrigerant and oil (at low pressure) enters the electric compressor 10 via the refrigerant inlet port 68, and leaves the electric compressor 10 (at high pressure) via the refrigerant outlet port 70 after being compressed by the compression device 18. Fig. 9 As shown in the cross-sectional view of FIG. 1 , the refrigerant passes through the electric compressor 10 along a refrigerant path 72. As shown, the refrigerant enters the refrigerant inlet port 68 and enters the intake volume 74 formed between the motor side 22A of the inverter housing 22 and the motor housing 24 adjacent the refrigerant inlet port 68. The refrigerant is then drawn through the motor section 16 and into the compressed intake volume 76 formed between the inner wall of the fixed scroll 26 and the orbiting scroll 66 (defined by the Fig.14A 92 in FIG.

[0064] like Fig. 9 and Fig.13 As shown, the fixed scroll 26 has a fixed scroll base 26A and a fixed scroll wrap 26B extending away from the fixed scroll base 26A toward the orbiting scroll 66. Figure 16A-16B As shown, the orbiting scroll 66 has an orbiting scroll base 66A and an orbiting scroll wrap 66B extending from the orbiting scroll base 66A toward the fixed scroll 26. The wraps 26A, 66A have trailing ends 26C, 66C adjacent to the outer edges of the respective scrolls 26A, 66B, and wrap inwardly toward the respective central ends 26D, 66D.

[0065] Respective tip seals 94 are located in slots 26E, 66E located at the top surfaces of the fixed scroll 26 and the orbiting scroll 66, respectively. The tip seals 94 are constructed of a flexible material such as polyphenylene sulfide (PPS) plastic. When assembled, the tip seals 94 are pressed against the opposing bases 26A, 66A to provide a seal therebetween. In one embodiment, the slots 26E, 66E are longer than the length of the tip seals 94 to provide room for adjustment / movement along the length of the tip seals 94.

[0066] refer to Figures 17A-17I , the mixed refrigerant enters the compression device 12 from the compressed air intake volume 76. Figures 17A-17I , a cross-sectional view of the top of the fixed scroll 16 and orbiting scroll 66 is shown.

[0067] As discussed in detail below, the fixed scroll wrap 16A and the orbiting scroll wrap 66A form compression chambers 80 into which low-pressure or unpressurized refrigerant enters from the compression device 12. As the orbiting scroll 66 rotates, these compression chambers 80 are closed and the volume of the compression chambers 80 is reduced to pressurize the refrigerant. At any one time during the cycle, one or more compression chambers 80 are at different stages in the compression cycle. The following description only relates to a set of compression chambers 80 during a complete cycle of the electric compressor 10.

[0068] Refrigerant enters compression chambers 80 formed between the orbiting scroll wrap 66A and the fixed scroll wrap 26A. Refrigerant is transported toward the center of these chambers during a cycle of the compressor 10. During one cycle of the electric compressor 10, the orbiting scroll 66 rotates in a circular motion indicated by arrow 78 formed by the relative position of the orbiting scroll 66 with respect to the fixed scroll 26.

[0069] exist Fig.17A , the position of the orbiting scroll 66 at the beginning of the cycle is shown. As shown, in this initial position, the trailing end portion 16B, 66B is spaced apart from the other scroll wrap 66B, 16A. At this point, the compression chamber 80 is open to the compressed intake volume 76, thereby allowing refrigerant to fill the compression chamber 80 from the compressed intake volume 76 at a low pressure. As the orbiting scroll 66 rotates along the path 78, the space between the trailing end portion 16A, 66A and the other scroll 66, 16 is reduced until the compression chamber 80 is open to the compressed intake volume 76 ( Figure 17B-17E As the orbiting scroll 66 continues to move along 78, the volume of the compression chamber 80 is further reduced, thereby Fig.17F -H) in the refrigerant pressurization. Figure 17I-Figure 1 As the orbiting scroll 66 continues to rotate, the two compression chambers 80 are combined into a single volume as shown in FIG8J. The volume is further reduced until the pressurized refrigerant is discharged from the compression device 18 (see below).

[0070] As discussed below, refrigerant enters chambers formed between the orbiting plate scroll 66 and the walls of the fixed plate scroll 26. Refrigerant is transported toward the center of these chambers during a cycle of the compressor 10. During one cycle of the electric compressor 10, the orbiting plate scroll 66 rotates in a circular motion indicated by arrow 78 formed by the relative position of the orbiting plate scroll 66 relative to the fixed plate scroll 26.

[0071] Return to Figure 1 , the front cover 28 forms an exhaust volume 82. The exhaust volume 82 is in communication with the refrigerant outlet port 70. As discussed in more detail below, the pressurized refrigerant leaves the compression device 18 through an orifice 84 in the fixed scroll 26 (see Fig.18C and Fig.18E ). The release of the pressurized refrigerant is controlled by a reed mechanism 86. In the illustrated embodiment, a single reed mechanism 86 is used. However, it should be noted that more than one reed mechanism may be used.

[0072] like Fig.18D and 18E As shown, in the illustrated embodiment, the reed mechanism 86 includes an exhaust reed 86A and a reed retainer 86B. The exhaust reed 86A is made of a flexible material such as steel. The properties such as material and strength are selected to control the pressure at which the pressurized refrigerant is released from the compression device 18. The reed retainer 86B is made of a rigid, inflexible material such as stamped steel. The reed retainer 86B controls or limits the maximum displacement of the exhaust reed 86A relative to the fixed scroll 26.

[0073] In the illustrated embodiment, the reed mechanism 86 is held or secured in place without separate fasteners. Fig.18E and 18F As shown, the reed mechanism 86 includes a pair of holes 86C that are configured to receive associated posts 84A on the fixed scroll 26. When the electric compressor 10 is assembled, the reed mechanism 86 is adjacent to the front cover 28 and is held in place by the front cover 28. Fig.18E As shown, the rear surface of the fixed scroll 26 includes a baffle 84B surrounding the orifice 84, which helps regulate the pressure of the refrigerant leaving the compression device 18. In addition, the debris collection slot 84B collects debris near the orifice 84 to prevent interference with the reed mechanism 86.

[0074] like Fig. 9 As shown, the path of the refrigerant through the electric compressor is indicated by dashed arrow 72 .

[0075] The electric compressor 10 utilizes oil (not shown) to provide lubrication between components of the compression device 18 and the motor 54, such as between the orbiting and fixed scrolls 66, 26, and within the ball bearings 62, 64. The oil mixes with the refrigerant within the compression device 18 and the motor 54 and exits the compression device 18 via the orifice 84. As discussed in more detail below, the oil is separated from the compressed refrigerant within the front cover 28 and returned to the compression device 18.

[0076] The oil separator 96 facilitates separation of the mixed oil and refrigerant. Typically, the oil separator 96 removes only some of the oil from the mixed oil and refrigerant. The separated oil is stored in an oil reservoir and circulated back through the compression device 18, where it is remixed with the refrigerant.

[0077] In the illustrated embodiment, the oil separator 96 is integrated into the front cover 28. The front cover 28 also defines an oil reservoir 98 that collects oil from the oil separator 96 before the oil is recirculated through the motor 54 and the motor cavity 56 and the compression device 18. In use, the electric compressor 10 is generally as shown in FIG. Figure 5 The orientation shown allows gravity to act as shown by arrow 106 and the oil collects in the reservoir 98. Fig. 9 , as shown by arrow 88, the general path oil travels from the bottom of the electric compressor 10, through the compression device 18, out of the orifice 84 to the exhaust volume 82 of the front cover 28, and back to the compression device 18. As shown, the oil is drawn upwardly back into the compression device 18 where it is mixed back into or with the refrigerant.

[0078] As described above, the refrigerant, which is actually a mixture of refrigerant and oil, enters the electric compressor 10 via the refrigerant inlet port 70. The mixture of oil and refrigerant is drawn into the motor section 16, thereby providing lubrication and cooling for the rotating parts of the electric compressor 10, such as the rotor 60, the drive shaft 90. The oil and refrigerant enter the interior of the motor 54 to lubricate the second ball bearing 64 through the rotational force within the motor section 16. The oil may hit the motor side 22A of the inverter housing 22. The refrigerant and oil are further guided into the ball bearing 62 by the motor side 22A, which will be discussed further below.

[0079] In the illustrated embodiment, the front cover 28 and the fixed scroll 26 are mounted to the motor housing 24 by a plurality of bolts 122 that are inserted through and threaded into corresponding holes in the motor housing 24. A fixed head gasket 110 and a rear head gasket 112 are located between the motor housing 24 and the fixed scroll 26 to provide a seal.

[0080] Concentric protrusion of swing link mechanism and drive shaft

[0081] Specific reference Figure 13-18B In a first aspect of the electric compressor 10 of the present disclosure, the electric compressor 10 includes a swing link mechanism 124, and the drive shaft 90 has a concentric protrusion 126. In one embodiment, the concentric protrusion 126 is formed integrally with the drive shaft 90. As discussed below, the swing link mechanism 124 is used to rotate the orbiting scroll 66 around the drive shaft 90 in an eccentric orbit.

[0082] In the prior art, the drive shaft is connected to the swing link mechanism by a drive pin and a separate eccentric pin, both of which are pressed into the drive shaft. The drive pin is used to rotate the swing link mechanism 124, which moves the orbiting scroll 66 along its eccentric orbit. The drive pin and the eccentric pin are inserted into corresponding holes at the end of the drive shaft. The eccentric pin is used to limit the articulation of the orbiting scroll 66 when the orbiting scroll 66 travels along the eccentric orbit. Neither the drive pin nor the eccentric pin is positioned along the central axis of the drive shaft. When the drive shaft rotates, the drive pin and the eccentric pin are under considerable stress. Therefore, both pins are made of hardened material, such as SAE 52100 bearing steel. In addition, the eccentric pin may require an aluminum bushing or other sliding bearing to prevent damage to the eccentric pin because the eccentric pin is used to limit the radial movement of the eccentric orbit of the orbiting scroll 66. Furthermore, the prior art eccentric pins require additional machining on the surface of the drive shaft 90, including precise holes for the drive pin and the eccentric pin.

[0083] As discussed in more detail below, the eccentric pin of the prior art is replaced with a concentric protrusion 90F.

[0084] In the illustrated embodiment, the scroll electric compressor 10 includes a housing 12, a refrigerant inlet port 68, a refrigerant outlet port 70, a drive shaft 90, a concentric protrusion 90F, a motor 54, a compression device 18, a swing linkage 124, a drive pin 126, and a ball bearing 108. The housing 12 defines an intake volume 74 and an exhaust volume 82. The refrigerant inlet port 68 is coupled to the housing 12 and is configured to be able to introduce refrigerant into the intake volume 74. The refrigerant outlet port 70 is coupled to the housing 12 and is configured to be able to allow compressed refrigerant to leave the scroll electric compressor 10 from the exhaust volume 82. The drive shaft 90 is located in the housing 12 and has a first end 90A and a second end 90B. The drive shaft 90 defines a central axis 90C and is centered on the central axis 90C.

[0085] The concentric protrusion 90F is located at the second end 90B of the drive shaft 90 and is centered on the central axis 90C. The concentric protrusion 90F extends away from the drive shaft 90 along the central axis 90C. The concentric protrusion 90F includes a drive pin hole 90E. The motor 54 is located within the housing 12 and is coupled to the drive shaft 90 so that the drive shaft 90 can be controlled to rotate around the central axis 90C. The drive pin 126 is located in the drive pin hole 90E and extends away from the drive shaft 90. The drive pin 126 is parallel to the concentric protrusion 90F.

[0086] The concentric pin 90F may also include an undercut structure 90G, and the outer surface may be a surface that is case hardened or that is treated with a coating or a bearing surface. The concentric pin 90F may be further processed simultaneously with the drive shaft 90 .

[0087] As explained above, the compression device 18 includes a fixed scroll 26 and an orbiting scroll 66. The fixed scroll 26 is located within the housing 12 and is fixed relative to the housing 12. The orbiting scroll 66 is coupled to the drive shaft 90. The orbiting scroll 66 and the fixed scroll 26 form a compression chamber 80 (see above) for receiving refrigerant from the intake volume 74 and compressing the refrigerant as the drive shaft 90 rotates about the central axis 90C. The orbiting scroll 66 has an inner circumferential surface 66E.

[0088] The swing link mechanism 124 is coupled to the drive shaft 90 and has a first hole 124A and a second hole 124B for receiving the concentric protrusion 90F and the drive pin 126. The swing link mechanism 124 also includes an outer circumferential surface 124C.

[0089] The ball bearing 108 is positioned between and abuts each of the inner circumferential surface 66E of the orbiting scroll 66 and the outer circumferential surface 124C of the swing link mechanism 124. The drive shaft 90, the drive pin 126, the orbiting scroll 66, and the swing link mechanism 124 are arranged to cause the orbiting scroll 66 to rotate in an eccentric orbit about the central axis 90C.

[0090] In one embodiment, the concentric protrusion 90F is integrally formed with the drive shaft 90. The drive shaft 90, the concentric protrusion 90F and the swing link mechanism 124 can be machined from steel. The concentric protrusion 90F formed simultaneously with the drive shaft 90 and in the same machining operation further improves manufacturing efficiency.

[0091] Figure 16G The enlarged view of a portion of the compression device 18 shown in FIG further shows the concentric protrusion 90F. The concentric protrusion 90F interacts with and guides the swing linkage 124. The concentric protrusion 90F is sized and machined to have a controlled tolerance with the first hole 124A to produce a controlled clearance that limits the radial movement of the eccentric track of the orbiting scroll 66. Unlike the prior art, the concentric protrusion 90F does not require a second pin or any additional machining operations. The concentric protrusion 90F also cooperates with the guide pin 128 and the groove 66G on the lower surface 66F of the orbiting scroll 66, which will be discussed further below.

[0092] The scroll motor compressor 10 includes an inverter section 14, a motor section 16, and a compression device 18. The motor section 16 includes a motor housing 54 defining a motor cavity 56. The compression section 18 includes a fixed scroll 26. The housing 12 at least partially forms the fixed scroll 26 and the motor housing 24.

[0093] Specific reference Fig.13 , Fig. 16B and Figure 18A-18F In the illustrated embodiment, the orbiting scroll 66 has a lower surface 66F. The lower surface 66F has a plurality of annular grooves 66G. The motor housing 24 includes a plurality of articulation guide pins 128. The guide pins 128 are located in the guide pin holes 66G and extend toward the compression device 18 and into the annular grooves 66G. The guide pins 128 are configured to limit the articulation of the orbiting scroll 66 when the orbiting scroll 66 orbits around the central axis 90C. In one embodiment, each of the annular grooves 66G includes an annular sleeve 118. The thrust plate 130 is located between the motor housing 24 and the fixed scroll 26 and provides an anti-wear surface between the motor housing 24 and the fixed scroll 26.

[0094] Discharge head design with oil separator

[0095] In a second aspect of the motor compressor 10 of the present disclosure, the motor compressor 10 includes an oil separator 96 located in the exhaust volume 82, the oil separator 96 being located in the exhaust volume 82 and being integrally formed with the discharge header or front cover 28. As discussed above, oil is used to provide lubrication between the moving parts of the motor compressor 10. During operation, the oil and the refrigerant mix together. Before the refrigerant leaves the motor compressor 10, the oil separator 96 is required to separate some of the oil from the mixture of oil and refrigerant.

[0096] Typically, refrigerant is released from the compression device 18 once for each rotation (or orbit) of the orbiting scroll 66. This produces a first-order pulsation in the compressed refrigerant released by the electric compressor 10. The relatively strong amplitude and low frequency of the pulsation generated in the refrigerant may excite other components (inside or outside the electric compressor 10), which may produce undesirable noise, vibration and harshness (NVH) and low durability conditions. The oil separator 96 of the second aspect (described below) is connected to the discharge chamber (see below) through a relatively small passage to produce a pressure drop between the chambers. This is used to allow the compressed refrigerant to flow smoothly out of the electric compressor 10. In addition, the oil separator 96 utilizes two parallel paths between the compression device 18 and the refrigerant outlet port 70 to reduce the net pressure drop while maintaining the reduction of the pulsation.

[0097] The oil separator 96 may include a series of partition walls 98A extending from the inner surface of the front cover 28. As shown, the partition walls 98A divide the exhaust volume 82 into a central discharge chamber 82A, two discharge side chambers 82B, an upper discharge chamber 82C, and an oil reservoir 98. The central discharge chamber 82A is adjacent to the reed mechanism 86 and receives the mixed pressurized refrigerant and oil from the compression device 18 through the slot 84 via the reed mechanism 86. The central discharge chamber 82 is in fluid communication with the two discharge side chambers 82B via corresponding side passages 100, and the side passages 100 are in fluid communication with the upper discharge chamber 82C and the oil reservoir 98 via the upper discharge passage 102 and the lower discharge passage 104, respectively.

[0098] In the illustrated embodiment, the oil separator 96 is formed in the discharge chamber 82 of the housing 12 between the compression device 18 and the refrigerant outlet port 70. As shown, the oil separator 96 includes a central discharge chamber 82A, a pair of discharge side chambers 82B, an oil reservoir 98, and an upper discharge chamber 82C. The central discharge chamber 82A is formed adjacent to the compression device outlet port or slot 84 for receiving the mixed oil and compressed refrigerant. A pair of discharge side chambers 82B are located on opposite sides of the central discharge chamber 82A and are connected to the central discharge chamber 82A via corresponding discharge side passages 100.

[0099] The side chamber 82B is configured to separate the mixed oil and compressed refrigerant. Typically, the mixed oil and compressed refrigerant leave the central discharge chamber 82 at a high speed through the side channel 100. When the mixed oil and compressed refrigerant hit the inner and outer walls of the corresponding side chamber 82B, the oil and compressed refrigerant are separated.

[0100] The oil reservoir 98 is located below the pair of side chambers and is connected to the pair of side chambers via corresponding lower discharge passages 104. The oil reservoir is configured to receive oil separated from the compressed refrigerant in the side chambers. Gravity acting on the oil assists in the separation, and the oil falls into the oil reservoir 98 through the lower discharge passage 104 located in the discharge side chamber 82B.

[0101] The upper discharge chamber 82C is formed above the pair of side chambers 82B and is connected to the side chambers 82B via corresponding upper discharge passages 102. The refrigerant rises through the upper discharge passage 102 located at the top of the discharge side chamber 82 after separation from the oil, and enters the upper discharge chamber 82 before passing through the refrigerant outlet port 70.

[0102] As shown, each discharge side passage 100 is configured to direct the mixed oil and compressed refrigerant toward the opposite inner wall of the corresponding side passage 82B. For example, the discharge side passage is generally at a 90 degree angle to the opposite wall of the discharge side chamber 82B.

[0103] In an alternative embodiment, if Fig. 20 As shown, each discharge side chamber 82B may include a side baffle 132 located at an inner portion of the corresponding discharge side chamber 82B. The discharge side passage 100 is configured to direct the mixed oil and compressed refrigerant toward the corresponding side baffle. The side baffle 132 forms a low pressure area in the discharge side chamber 82B on the rear side opposite to the discharge passage 100, which helps separate the oil and refrigerant. The low pressure area can further assist gravity and reduce the oil from being transported upward toward the upper discharge passage 102. The discharge side passage 100 may include a downward angle, which can further assist gravity acting on the oil and further increase the distance that the oil falls out of the compressed mixture by directing the discharge of the mixture toward the lower area of ​​the discharge side chamber 82B adjacent to the lower discharge passage 104, and separate the oil downward and away from the high-speed compressed refrigerant entering the upper discharge passage 102 by creating a longer tortuous path. Additionally, the side baffles 132 may be arranged to create an impact surface that is perpendicular to the angled discharge flow path of the oil and refrigerant exiting the discharge side passage 100. The vertical impact surface on the side baffles 132 creates additional turbulence to the discharge mixture, and the lower pressure area behind the side baffles 132 may further increase the gravity effect on the heavier oil to separate the oil internally and direct it into the lower discharge passage 104.

[0104] In addition, if Fig. 20 As shown, the oil reservoir 98 may include an oil reservoir baffle 134 located below each lower discharge passage 104. The oil reservoir baffle 134 helps prevent the oil within the oil reservoir 98 from being drawn from the oil reservoir back into the discharge side chamber 82B. The side baffles 132 and the oil reservoir baffle 134 may be used in combination or alone to reduce the oil from traveling up the wall of the discharge side chamber 82B and further reduce the suction or venturi effect that may be generated by the high velocity flow of the refrigerant exiting through the upper discharge passage 102 by creating a low pressure side.

[0105] Vortex bearing oil port

[0106] In a third aspect of the electric compressor 10 of the present disclosure, an electric compressor 10 having a scroll bearing oil injection orifice is provided. As discussed above, the compression device 18 of the present disclosure includes a ball bearing 108. In the illustrated embodiment, the ball bearing 108 is located between the swing link mechanism 124 and the orbiting scroll 66. However, due to the location of the ball bearing 108 within the compression device 18, there may be limited oil delivery to the ball bearing 108, thereby reducing durability.

[0107] The scroll electric compressor 10 may include a housing 12, a refrigerant inlet port 68, a refrigerant outlet port 70, an inverter module 144, a motor 54, a drive shaft 90, and a compression device 18. The housing 12 defines an intake volume 74 and an exhaust volume 82. The refrigerant inlet port 68 is coupled to the housing 12 and is configured to be able to introduce refrigerant into the intake volume 74. The refrigerant outlet port 70 is coupled to the housing 12 and is configured to be able to allow compressed refrigerant to leave the scroll electric compressor 10 from the exhaust volume 82. The inverter module 144 is mounted in the housing 12 and is suitable for converting direct current into alternating current. The motor 54 is mounted inside the housing 12. The drive shaft 90 is coupled to the motor 54. As the drive shaft 90 is rotated by the motor 54, the compression device 18 receives refrigerant from the intake volume 74 and compresses the refrigerant. The compression device 18 includes the fixed scroll 26 , the orbiting scroll 66 , the swing linkage 124 , the ball bearing 108 , and the pin 136 .

[0108] The fixed scroll 26 is located within the housing 12 and is fixed relative to the housing 12. The orbiting scroll 66 is coupled to the drive shaft 90. The orbiting scroll 66 and the fixed scroll 26 form a compression chamber 80 for receiving refrigerant from the intake volume 72 and compressing the refrigerant as the drive shaft 90 rotates about the central axis 90C. The orbiting scroll 66 has a first side (or lower surface) 66F and a second side (or upper surface) 66G. The orbiting scroll 66 has an oil hole 140 that passes through the orbiting scroll 66 from the first side 66F to the second side 66G.

[0109] The swing link mechanism 124 is coupled to the drive shaft 90. The ball bearing 108 is located between and adjacent to the orbiting scroll 66 and the swing link mechanism 124, respectively. The drive shaft 90, the orbiting scroll 66, and the swing link mechanism 124 are arranged to cause the orbiting scroll 66 to orbit around the central axis 90C in an eccentric orbit.

[0110] like Fig. 16C As shown, the top end of the orbiting scroll 66 includes a plug 136 and has an oil orifice 138. The plug 136 may be press-fit into an oil hole 140 of the orbiting scroll 66. The oil orifice 138 is configured to allow oil or compressed refrigerant to pass through the orbiting scroll 66 to the ball bearing 108 at a controlled flow rate.

[0111] The size of the oil orifice 138 can be adjusted according to the specifications of the electric compressor 10. For example, given the specifications of the electric compressor 10, the diameter of the oil orifice 138 can be selected so as to only allow oil to pass through and limit the pressure equalization between the first side and the second side of the orbiting scroll 66. By using a separate plug 136, rather than machining the oil orifice 138 directly in the orbiting scroll 66, manufacturing efficiencies can be achieved. And the plug 136 can have an oil orifice 138 that is specially designed and adjusted to allow oil flow and refrigerant flow to increase or decrease according to the diameter and geometry of the oil orifice 138.

[0112] like Figure 16D-16E As shown, in one embodiment, the oil orifice 138 may have a first hole 138A and a second hole 138B, wherein the diameter of the first hole 138A is smaller than the diameter of the second hole 138B. For example, in one application of this embodiment, the first hole 138A has a diameter of about 0.3 mm. The second hole 138B has a diameter greater than the diameter of the first hole 138A and is only used to shorten the length of the first hole 138A. The flow of oil and coolant is designed to provide heat and lubricant to the ball bearing 108, which supports the radial force generated by the eccentric track of the orbiting scroll 66.

[0113] In addition, as discussed above, the orbiting scroll 66 has an orbiting scroll base 66A and an orbiting scroll wrap 66B. The orbiting scroll wrap 66B may have an orbiting scroll tail end 66C and an orbiting scroll center end 66D. As shown, the oil hole 140 is located in the orbiting scroll center end 66D. The plug 136 may be fixed to the oil hole 140 by press fitting or any other method of fixing the plug 136.

[0114] like Fig. 9 As shown, oil orifice 138 allows oil (and refrigerant) to travel from discharge chamber 82 to ball bearing 108 along bath 73 (which may be referred to as a “nosebleed” path).

[0115] Bearing oil connecting hole

[0116] In a fourth aspect of the electric compressor of the present disclosure, an electric compressor 10 having a bearing oil connecting hole is provided. As discussed above, in the illustrated embodiment, the drive shaft 90 is rotated by the motor 54 to controllably actuate the compression device 18. The drive shaft 90 has a first end 90A and a second end 90B. The housing 10 of the electric compressor 10 forms a first drive shaft support member 22B and a second drive shaft support member 24A. In the illustrated embodiment, the first drive shaft support member 22B is formed in the motor side 22 of the inverter housing 22A, and the second drive shaft support member 24A is formed in the motor housing 24. The first ball bearing 62 and the second ball bearing 64 are located in the first drive shaft support member 22B and the second drive shaft support member 24A.

[0117] The position of the first drive shaft support member 22B is not a circulation area of ​​the refrigerant (and oil). This can result in a poor lubrication condition and affect the durability of the electric compressor 10.

[0118] like Fig.16F As shown, the first drive shaft support member 22B may include one or more holes 22C to allow oil and refrigerant to enter the first drive shaft support member 22B and lubricate the first ball bearing 62 .

[0119] In the illustrated embodiment, the scroll electric compressor 10 includes a housing 12 , a first ball bearing 62 , a second ball bearing 64 , a refrigerant inlet port 68 , a refrigerant outlet port 70 , an inverter module 44 , a motor 54 , a drive shaft 90 , and a compression device 18 .

[0120] The housing 12 defines an intake volume 74 and an exhaust volume 82, and includes a first drive shaft support member 22B and a second drive shaft support member 24A. The first ball bearing 62 is located in the first drive shaft support member 22B. The first drive shaft support member 22B of the housing 12 includes an oil communication hole 22C for allowing oil to enter the first ball bearing 62.

[0121] The second ball bearing 64 is located in the second drive shaft support member 24A. The refrigerant inlet port 68 is connected to the housing 12 and is configured to be able to introduce refrigerant into the intake volume 74. The refrigerant outlet port 70 is connected to the housing 12 and is configured to be able to allow compressed refrigerant to leave the scroll electric compressor 10 from the exhaust volume 82. The inverter module 144 is installed inside the housing 12 and is suitable for converting direct current into alternating current. The motor 54 is installed inside the housing 12. The drive shaft 90 is connected to the motor 54. The drive shaft 90 has a first end 90A and a second end 90B. The first end 90A of the drive shaft 90 is positioned in the first bearing 62, and the second end 90B of the drive shaft 90 is positioned in the second bearing 64. As the drive shaft 90 is rotated by the motor 54, the compression device 18 receives refrigerant from the intake volume 74 and compresses the refrigerant. As discussed above, in the illustrated embodiment, the first drive shaft support member 22 can be formed on the motor side 22A of the inverter housing 22. The rotational motion within the motor section 16 of the compression device 18 creates a flow path and movement of oil from the oil reservoir 98, such as Fig. 9 As shown in the figure, the oil flows from the oil reservoir 98 toward the motor section 16 and continues to flow toward the stator 58 and the rotor 60. The rotational motion of the orbiting scroll, the rotor and the drive shaft draws the oil upward to mix with the input flow of the refrigerant path 72. The rotational motion of the rotor 60 and the drive shaft 90 will further push the oil toward the motor side 22A of the inverter housing 22. The motor side 22A also includes a series of ribs 22D, such as Fig.16F As shown. The rib 22D provides the rigidity required for supporting the first drive shaft support member 22 and allows the ridged backing and recess to secure the first bearing 62. The inverter housing 22 also defines an oil cavity 22E, and the oil collected between the ribs 22D is guided downward by gravity and enters the oil cavity 22E. The ribs 22D and the inclined surfaces of the motor side 22A cooperate to capture and guide the oil splashed or pushed onto the motor side 22A by the rotor 60 or the drive shaft 90 to help increase the oil flowing into the oil cavity 22E and the first bearing 62. Fig.16F Only one oil communication hole 22C is shown, but it should be understood that additional oil communication holes 22C may be included above and between the ribs 22D on the motor side 22A of the inverter housing 22. For example, in the illustrated embodiment, the communication hole 22C has a diameter of 3.5 mm, and the motor side 22A includes an inclined wall between the ribs 22D. In addition, the motor side 22A may include an outer oil collection area or recess 22F surrounding the communication hole 22C.

[0122] Dome-shaped inverter cover

[0123] In the fifth aspect of the electric compressor 10 of the present disclosure, the scroll electric compressor 10 is configured to be able to compress refrigerant. The scroll electric compressor 10 includes a housing 12, a refrigerant inlet port 68, a refrigerant outlet port 70, an inverter module 44, a motor 54, a drive shaft 90, a compression device 18 and an inverter cover 20. The housing 12 defines an intake volume 70 and an exhaust volume 82. The housing 12 has a generally cylindrical shape and a central axis 90C. The refrigerant inlet port 68 is coupled to the housing 12 and is configured to be able to introduce refrigerant into the intake volume 70. The refrigerant outlet port 82 is coupled to the housing 12 and is configured to be able to allow compressed refrigerant to leave the scroll electric compressor 10 from the exhaust volume 82.

[0124] The inverter module 44 is mounted inside the housing 12 and is adapted to convert direct current into alternating current. The motor 54 is mounted inside the housing 12. The drive shaft 90 is coupled to the motor 54. The compression device 18 is coupled to the drive shaft 90 and is configured to receive refrigerant from the intake volume and compress the refrigerant as the drive shaft 90 is rotated by the motor 54.

[0125] As discussed above, the compression device 18 may rotate at high speeds (>2000 RPM), which may result in undesirable noise, vibration and harshness (NVH) and low durability conditions. In the prior art, the inverter cover 20 is typically flat and tends to amplify and / or concentrate vibrations from the compression device 18 .

[0126] like Figure 3A-3D As shown, in order to disperse vibration rather than concentrate vibration from the compression device 18 , the inverter rear cover 20 of the scroll type electric compressor 10 of the fifth aspect of the present disclosure is provided with a substantially curved or domed profile.

[0127] As shown in the figure, specifically, Figure 1 , Figure 3A-3B and Figure 6 As shown, the inverter cover 20 is located at one end of the scroll electric compressor 10, and includes a first portion 20A and a second portion 20B. The first portion 20A includes a vertex or vertex portion 20C, and is substantially perpendicular to the central axis 90C, and has a vertex 20C and a periphery 20D. The first portion 20A has a relatively dome-shaped shape, so that the inverter cover 20 has a curved profile from the vertex 20C toward the periphery 20D. The amount and position of the bend can be determined or limited by other considerations, such as packaging constraints, i.e., the space in which the scroll electric compressor 10 must fit, and by the placement of internal components, i.e., position and size constraints. The first portion 20A may also need to be combined with other features, for example, holes for receiving fastening bolts. The second portion 20B may include a portion of the inverter cover 20 that is located around the periphery of the inverter cover, which is not dome-shaped, i.e., relatively flat.

[0128] exist Figure 3B , the back side of the inverter cover 20 may include a plurality of radial ribs 20E extending outwardly from the central circular rib 20F to provide rigidity and support for the curved first portion 20A of the inverter back cover 20. As shown, the radial ribs 20E are not equally spaced around the central circular rib 20F. The inverter back cover 20 may also include additional ribs 20G to add additional strength.

[0129] refer to Figure 3C and Figure 3D , shows an alternative embodiment of the inverter cover 20. In some applications, the inverter cover 20, particularly the first portion 20A, may need to be modified to take into account external constraints, such as packaging or size constraints. In the embodiment shown, the embodiment shown includes a channel 20H through the first portion 20A, which is necessary to accommodate external support structures.

[0130] The foregoing invention has been described in accordance with relevant legal standards, and therefore the description is illustrative rather than limiting in nature. Variations and modifications to the disclosed embodiments will be apparent to those skilled in the art and fall within the scope of the invention.

Claims

1. A scroll electric compressor configured to compress a refrigerant, comprising: a housing defining an intake volume and an exhaust volume, the housing including a first drive shaft support member and a second drive shaft support member, the housing including an inverter housing, the inverter housing having a motor side adjacent the intake volume, the first drive shaft support member formed by the inverter housing and located on the motor side thereof, the first drive shaft support member being recessed, the motor side of the housing forming an oil cavity, the oil cavity being configured to collect oil from the intake volume; a first ball bearing located within the first drive shaft support member, the first drive shaft support member of the housing including an oil communication hole for allowing oil from the oil chamber to enter the first ball bearing; a second ball bearing positioned within the second drive shaft support member; a refrigerant inlet port coupled to the housing and configured to introduce refrigerant into the intake volume; a refrigerant outlet port coupled to the housing and configured to allow compressed refrigerant to exit the scroll electric compressor from the exhaust volume; an inverter module, which is installed in the housing and is suitable for converting direct current into alternating current; a motor mounted in the housing; a drive shaft coupled to the motor, the drive shaft having a first end and a second end, the first end of the drive shaft being positioned within the first ball bearing, the second end of the drive shaft being positioned within the second ball bearing; and A compression device is coupled to the second end of the drive shaft for receiving refrigerant from the intake volume and compressing the refrigerant as the drive shaft is rotated by the motor.

2. The scroll electric compressor according to claim 1 further includes an inverter section, wherein the inverter section includes the inverter housing and the inverter back cover, the inverter housing and the inverter back cover form an inverter cavity, and the inverter module is installed in the inverter cavity.

3. A scroll electric compressor configured to compress a refrigerant, comprising: a housing defining an intake volume and an exhaust volume, the housing including a first drive shaft support member and a second drive shaft support member; a first ball bearing located within the first drive shaft support member, the first drive shaft support member of the housing including an oil communication hole for allowing oil from the oil chamber to enter the first ball bearing; a second ball bearing positioned within the second drive shaft support member; a refrigerant inlet port coupled to the housing and configured to introduce refrigerant into the intake volume; a refrigerant outlet port coupled to the housing and configured to allow compressed refrigerant to exit the scroll electric compressor from the exhaust volume; an inverter module, which is installed in the housing and is suitable for converting direct current into alternating current; a motor mounted in the housing; a drive shaft coupled to the motor, the drive shaft having a first end and a second end, the first end of the drive shaft being positioned within the first ball bearing, the second end of the drive shaft being positioned within the second ball bearing; a compression device coupled to the second end of the drive shaft for receiving refrigerant from the intake volume and compressing the refrigerant as the drive shaft is rotated by the motor; a fixed scroll disposed within the housing and fixed relative to the housing, and an orbiting scroll coupled to the drive shaft, the orbiting scroll and the fixed scroll forming a compression chamber for receiving refrigerant from the intake volume and compressing the refrigerant as the drive shaft rotates about a central axis, the orbiting scroll having a first side and a second side and an oil hole passing through the orbiting scroll from the first side to the second side, a swing link mechanism coupled to the drive shaft, a ball bearing located between the orbiting scroll and the swing link mechanism and adjacent to the orbiting scroll and the swing link mechanism, respectively, the drive shaft, the orbiting scroll and the swing link mechanism being arranged to cause the orbiting scroll to orbit around the central axis in an eccentric orbit, and A pin having an oil aperture and press fit within the oil hole of the orbiting plate scroll, wherein the oil aperture is configured to allow oil to pass through the orbiting plate scroll to the ball bearing.

4. The scroll type electric compressor according to claim 3, wherein: The orbiting scroll has an orbiting scroll base and an orbiting scroll wrap, wherein the orbiting scroll wrap includes an orbiting scroll tail end and an orbiting scroll center end, wherein the oil hole is located in the orbiting scroll center end.

5. The scroll type electric compressor according to claim 1, wherein: The housing includes a motor section, the motor having a motor housing defining a motor cavity for accommodating the motor, and the compression device includes a fixed plate scroll forming a part of the housing.

6. The scroll type electric compressor according to claim 5, wherein: The fixed scroll is mounted to the motor housing, the compression device includes an orbiting scroll having a lower surface with a plurality of annular grooves, wherein the motor housing includes a plurality of hinge guide pin holes, and also includes a plurality of guide pins located in the guide pin holes and extending toward the compression device and entering the annular grooves, the guide pins being configured to limit the articulation of the orbiting scroll when the orbiting scroll orbits around the central axis.

7. The scroll-type electric compressor of claim 6, including a plurality of annular inserts positioned within the annular groove.

8. The scroll electric compressor according to claim 1, wherein: The housing includes a front cover that defines the exhaust volume, wherein the scroll electric compressor uses oil to lubricate the motor, the drive shaft and components of the compression device, and the scroll electric compressor also includes an oil separator for separating the mixed oil and refrigerant when the mixed oil and refrigerant leave the compression device and enter the exhaust volume.

9. A scroll electric compressor having a central axis and configured to compress a refrigerant, the scroll electric compressor comprising: a housing defining an intake volume and an exhaust volume; a refrigerant inlet port coupled to the housing and configured to introduce refrigerant into the intake volume; a refrigerant outlet port coupled to the housing and configured to allow compressed refrigerant to exit the scroll electric compressor from the exhaust volume; An inverter section comprising: an inverter housing having a motor side adjacent to the intake volume and including a first drive shaft support member on the motor side, the first drive shaft support member being recessed, the motor side of the inverter housing forming an oil cavity configured to collect oil from the intake volume, an inverter rear cover, which is connected to the inverter housing and forms an inverter cavity, An inverter module, which is installed in the inverter cavity and is suitable for converting direct current into alternating current; The motor section includes: a motor housing forming a motor cavity and mounted to the inverter housing, the motor housing having a second drive shaft supporting member, a drive shaft located within the motor housing, having a first end and a second end and defining a central axis, a first ball bearing located in the first drive shaft support member, the first drive shaft support member of the housing having an oil communication hole for allowing oil to enter the first ball bearing from the oil cavity, a second ball bearing located within the first drive shaft support member, and a motor located within the motor housing to controllably rotate the drive shaft about the central axis, and A compression device is coupled to the second end of the drive shaft for receiving refrigerant from the intake volume and compressing the refrigerant as the drive shaft is rotated by the motor.

10. A scroll electric compressor having a central axis and configured to compress a refrigerant, the scroll electric compressor comprising: a housing defining an intake volume and an exhaust volume; a refrigerant inlet port coupled to the housing and configured to introduce refrigerant into the intake volume; a refrigerant outlet port coupled to the housing and configured to allow compressed refrigerant to exit the scroll electric compressor from the exhaust volume; An inverter section comprising: an inverter housing including a first drive shaft support member, an inverter rear cover, which is connected to the inverter housing and forms an inverter cavity, An inverter module, which is installed in the inverter cavity and is suitable for converting direct current into alternating current; The motor section includes: a motor housing forming a motor cavity and mounted to the inverter housing, the motor housing having a second drive shaft supporting member, a drive shaft located within the motor housing, having a first end and a second end and defining a central axis, a first ball bearing located in the first drive shaft support member, the first drive shaft support member of the housing having an oil communication hole for allowing oil to enter the first ball bearing, a second ball bearing located within the first drive shaft support member, and a motor located within the motor housing to controllably rotate the drive shaft about the central axis, and a compression device for receiving refrigerant from the intake volume and compressing the refrigerant as the drive shaft is rotated by the motor; a fixed scroll disposed within the housing and fixed relative to the housing; an orbiting plate scroll coupled to the drive shaft, the orbiting plate scroll and the fixed plate scroll forming a compression chamber for receiving refrigerant from the intake volume and compressing the refrigerant as the drive shaft rotates about the central axis, the orbiting plate scroll having a first side and a second side and an oil hole passing through the orbiting plate scroll from the first side to the second side; a swing linkage coupled to the drive shaft; a ball bearing located between the orbiting scroll and the swing link mechanism and adjacent to the orbiting scroll and the swing link mechanism, respectively, the drive shaft, the orbiting scroll and the swing link mechanism being arranged to cause the orbiting scroll to orbit around the central axis in an eccentric orbit; and, A pin having an oil aperture and press fit within the oil hole of the orbiting plate scroll, wherein the oil aperture is configured to allow oil to pass through the orbiting plate scroll to the ball bearing.

11. The scroll type electric compressor according to claim 10, wherein: The fixed scroll is mounted to the motor housing, wherein the orbiting scroll has a lower surface having a plurality of annular grooves, wherein the motor housing includes a plurality of hinge guide pin holes, and also includes a plurality of guide pins located in the guide pin holes and extending toward the compression device and entering the annular grooves, wherein the guide pins are configured to limit the articulation of the orbiting scroll when the orbiting scroll orbits around the central axis.

12. The scroll-type electric compressor of claim 11, including a plurality of annular inserts positioned within the annular groove.

13. The scroll electric compressor according to claim 10, wherein the housing comprises a front cover, wherein: The front cover defines the exhaust volume, wherein the scroll electric compressor utilizes oil to lubricate the motor, the drive shaft and components of the compression device, and the scroll electric compressor also includes an oil separator for separating the mixed oil and refrigerant when the mixed oil and refrigerant leave the compression device and enter the exhaust volume.

14. The scroll type electric compressor according to claim 1, wherein: The inverter housing has a plurality of support ribs on a motor side thereof, and the oil chamber is formed by a pair of adjacent support ribs and an outer surface of the first drive shaft support member.

15. The scroll type electric compressor according to claim 9, wherein: The inverter housing has a plurality of support ribs on a motor side thereof, and the oil chamber is formed by a pair of adjacent support ribs and an outer surface of the first drive shaft support member.

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