WO2018054292A1

WO2018054292A1 - Dual-drive compressor

Info

Publication number: WO2018054292A1
Application number: PCT/CN2017/102321
Authority: WO
Inventors: 陈雪峰; 杨应葵; 易夏辉; 任光远
Original assignee: 比亚迪股份有限公司
Priority date: 2016-09-21
Filing date: 2017-09-19
Publication date: 2018-03-29

Abstract

A dual-drive compressor, comprising: a casing assembly (1000); a scroll assembly (3000), a crankshaft (2000) and a motor assembly (5000) which are located inside the casing assembly (1000); an electrical control assembly (6000) mounted outside the casing assembly (1000); and a clutch assembly (4000) connected to the crankshaft (2000). The electrical control assembly (6000) is detachably mounted outside the casing assembly (1000), and an electrical connection is achieved between the electrical control assembly (6000) and the motor assembly (5000) by means of a pluggable electrical contact. The compressor can be in a seamless connection during power switching, avoiding loss of air conditioning function and improving user experience.

Description

Double drive compressor

Technical field

The present disclosure relates to a compressor, and in particular to a dual drive compressor.

Background technique

With the development of the new energy automobile industry, the application of hybrid vehicles is more and more widespread. In the use of hybrid vehicles, the battery power is consumed in the pure electric driving mode. When the vehicle is feeding, the remaining power cannot be provided. Electric air conditioning compressors, air conditioning systems can not work properly, the interior environment comfort is worse. In addition, the lubricating effect of the conventional fuel compressor is poor, and the lubricating oil circuit can only rely on a little refrigerating oil carried by the refrigerant to return to the compressor in the form of gas-liquid two-phase, and the durability of the operating mechanism is not good.

Summary of the invention

It is an object of the present disclosure to provide a dual drive compressor in which the electronic control assembly has the advantages of high interchangeability and convenient assembly and disassembly.

In order to achieve the above object, the present disclosure provides a dual drive compressor including a housing assembly, a scroll assembly, a crankshaft and a motor assembly located inside the housing assembly, mounted outside the housing assembly An electronic control assembly, and a clutch assembly coupled to the crankshaft, the electronic control assembly is detachably mounted to an outer side of the housing assembly, and the electronically controlled assembly and the motor assembly are Electrical connections are made through pluggable electrical connectors.

In some embodiments, the electronic control assembly includes an electrically controlled housing and a control element housed in the electrically controlled housing, the electrically controlled housing being positively coupled to the outside of the housing assembly.

In some embodiments, the electrical connector of the electronic control assembly includes a three-phase connector, and the electrical connector of the motor assembly includes a three-phase terminal, and the three-phase terminal and the three-phase connector are Plug and connect.

In some embodiments, the control element includes an electronically controlled PCB board that is coupled to the electronically controlled PCB board and extends outwardly through the electronically controlled housing.

In some embodiments, the casing assembly is provided with a motor wiring hole extending from the motor wiring hole, and the three-phase terminal is electrically connected to the motor assembly.

In some embodiments, the three-phase terminal includes a first mounting disk embedded in the motor wiring hole, a first pin inserted in the first mounting disk, the first pin Electrically connected to the motor assembly, the three-phase plug The connector includes a first female terminal that can wrap the first pin in an interference fit, the first female terminal being fixedly coupled to the electronic control PCB board by a first pin.

In some embodiments, the motor wiring hole is formed with a third stepped surface, one end of the first mounting disk abuts on the third stepped surface, and the other end is fixed on the casing assembly. The third circlip limit.

In some embodiments, a first sealing ring is disposed between the first mounting disk and the motor wiring hole.

In some embodiments, a first insulator sleeved on the first pin is disposed between the first pin and the first mounting pad.

In some embodiments, the portion of the first pin that protrudes from the first mounting disk is sleeved with a second insulator.

In some embodiments, a portion of the first pin that is inserted into the housing assembly is sleeved with a third insulator.

In some embodiments, the outer side of the electronically controlled housing is spaced apart from fasteners to secure the housing assembly and the electronically controlled assembly.

In some embodiments, the electronic control housing includes a first base and a first cover, a first sealing gasket is disposed between the first base and the first cover, and the electronic control housing is further disposed Low voltage wiring and high voltage wiring.

In some embodiments, the outer side of the electrically controlled housing corresponds to the location of the low pressure chamber of the dual drive compressor covered with a layer of thermally conductive material.

In some embodiments, in the plugged state, a second sealing ring is disposed between the electronically controlled housing and the housing assembly corresponding to the position of the motor wiring hole.

In some embodiments, the crankshaft includes a front axle and a rear axle that are coaxially coupled, and a speed increasing portion is disposed between the front axle and the rear axle such that the rotational speed of the rear axle is greater than the rotational speed of the front axle.

In some embodiments, the speed increasing portion is a planetary gear mechanism.

In some embodiments, the speed increasing portion includes a sun gear disposed at a front end of the rear axle and rotating with the rear axle, a planetary gear disposed at a rear end of the front axle and rotating with the front axle The planetary gear rotates in a toothed manner about the sun gear, and the outer side of the planetary gear is further provided with a fixed wheel that is cooperating with the planetary gear, and the fixed wheel is fixed to the casing assembly. The inner wall.

In some embodiments, the rear end of the front axle is formed with a planet carrier that is evenly spaced circumferentially spaced with an eccentric pin on which the planet gears are mounted.

In some embodiments, the planet carrier includes a center disk, and a mounting plate that projects outwardly from a radial direction of the center disk, the eccentric pin being disposed on the mounting plate.

In some embodiments, the interior of the casing assembly is partitioned into a main cavity and an auxiliary cavity distributed in the axial direction by a barrier wall sleeved on the crankshaft, the auxiliary cavity being formed in the casing. Between the front end cover and the barrier wall, the front axle is formed in the clutch assembly, the speed increasing portion is formed in the auxiliary cavity, and the rear axle is formed in the main body In the cavity.

Through the above technical solution, the electronic control assembly and the casing assembly of the compressor are connected by the pluggable electrical connector, which has the advantages of high interchangeability and convenient disassembly and assembly, and can save the after-sales maintenance cost.

Other features and advantages of the present disclosure will be described in detail in the detailed description which follows.

DRAWINGS

The drawings are intended to provide a further understanding of the disclosure, and are in the In the drawing:

1 is a front elevational view of a dual drive compressor in accordance with an embodiment of the present disclosure;

Figure 2 is a cross-sectional view of the dual drive compressor of Figure 1 taken along line A-A;

3 is a schematic structural view of a dual drive compressor according to another embodiment of the present disclosure;

Figure 4 is a partial enlarged view of the portion T of Figure 3, wherein the view is rotated by 90 degrees;

Figure 5 is a cross-sectional view of the portion of Figure 4 taken along line B-B;

6 is a schematic structural view of a front axle according to an embodiment of the present disclosure;

7 is a schematic structural view of a planet carrier according to an embodiment of the present disclosure;

8 is a schematic structural view of a resolver according to an embodiment of the present disclosure;

Figure 9 is a cross-sectional view of the cyclone of Figure 8 taken along line C-C;

10 is a schematic structural view of a cabinet assembly according to an embodiment of the present disclosure;

11 is a schematic view showing the assembly of a support disk and a crankshaft according to an embodiment of the present disclosure;

12 is a schematic structural view of an electronic control assembly according to an embodiment of the present disclosure;

13 is a schematic view showing the connection of an electronic control assembly and a casing assembly according to an embodiment of the present disclosure;

Figure 14 is a partial enlarged view of a portion P in Figure 13;

15 is a schematic view showing the connection of an electric control assembly and a casing assembly according to another embodiment of the present disclosure;

Figure 16a is a partial enlarged view of the portion Q of Figure 15;

Figure 16b is an exploded view of a resolver plug in accordance with an embodiment of the present disclosure.

detailed description

The specific embodiments of the present disclosure will be described in detail below with reference to the accompanying drawings. It is to be understood that the specific embodiments described herein are not to be construed

In the present disclosure, for the convenience of description, the orientation words used, such as "front and rear", are defined by the public according to a specific structure, for example, in the axial direction of the crankshaft, for the convenience of description. Direction, with clutch One end of the assembly connection is the front, and the opposite end is the rear; the "inside and outside" are generally for the contour of the corresponding component itself.

The present disclosure provides a dual drive compressor. The basic structure and operation of the dual drive compressor are first described below in conjunction with FIGS. 1 and 2.

As shown in FIGS. 1 and 2, the dual drive compressor includes a casing assembly 1000, a crankshaft 2000 located inside the casing assembly 1000, a scroll assembly 3000, and a motor assembly 5000, mounted on the casing. The external electronic control assembly 6000 is 1000, and the clutch assembly 4000 is connected to the crankshaft 2000. It should be noted that, as shown in FIG. 2, the internal portion of the crankshaft 2000 located in the casing assembly 1000 means that the main portion of the crankshaft 2000 is located inside the casing assembly 1000, and the crankshaft 2000 extends out of the casing assembly 1000. Partially coupled to the clutch assembly 4000.

The dual drive compressor in the present disclosure is exemplified by a scroll compressor. In this type of compressor, the scroll assembly 3000 includes a stationary plate 3100 and a moving plate 3200. During the operation of the compressor, the rotation of the crankshaft 2000 drives the movable disc 3200 to perform eccentric motion. Under the eccentric rotation, the moving disc type line and the static disc type line form a crescent cavity with a gradually decreasing volume (ie, a compression chamber of the scroll compressor). The refrigerant entering the compression chamber from the air inlet is continuously compressed in the process, and the finally formed high-temperature and high-pressure gas is discharged from the exhaust port, thereby completing the compression of the refrigerant.

In the dual drive compressor provided by the present disclosure, the crankshaft 2000 can be driven by the motor assembly 5000, that is, the electric drive mode, or the clutch assembly 4000 can transmit the drive force, that is, the mechanical drive mode. The structure, principle and improvement of the mechanical drive mode will be described in detail below.

Mechanical drive mode

As shown in FIG. 3, the clutch assembly 4000 primarily includes a pulley 4300, a coil 4100, and a drive plate 4200. The pulley 4300 is rotatably mounted on the front end cover 1400 of the cabinet assembly 1000 by bearings. The drive plate 4200 is rotatably coupled to the crankshaft 2000. In operation, the coil 4100 in the clutch assembly 4000 is energized to produce an electromagnetic attraction that engages the pulley 4300 and the drive plate 4200 such that the pulley 4300 can rotate the crankshaft 2000 to drive the compressor to operate. The pulley 4300 generates a driving force by being coupled to the vehicle engine drive wheel, and the dual drive compressor in the mechanical drive mode is the same as the conventional mechanical compressor drive mode, the specific drive form of which is well known to those skilled in the art, Do not make a detailed description.

When the crankshaft 2000 provided by the present disclosure adopts the mechanical driving mode, in order to improve the working efficiency, as shown in FIG. 3, the crankshaft 2000 may include a front axle 2100 and a rear axle 2200 which are coaxially connected, and a front axle 2100 and a rear axle 2200 may be provided. There is a speed increasing portion 2300 such that the rotational speed of the rear axle 2200 is greater than the rotational speed of the front axle 2100, so that the transmission ratio of the rear axle 2200 to the engine driving wheel can be increased. That is, compared with the integrated crankshaft in the prior art, when the engine outputs a certain torque, the rotation speed of the rear axle 2200 for driving the scroll assembly 3000 is increased, and the engine to controller can be reduced. The voltage resistance and current resistance of the components are required, and the compressor operating efficiency is improved, and the advantages of high speed and high efficiency of the scroll compressor are exerted.

The speed increasing portion 2300 can be realized in various forms. As an embodiment, the present invention uses a planetary gear mechanism for transmission, which is suitable for the shafting system, and the planetary gear mechanism has a compact structure, small volume, small mass, and large bearing capacity. The transmission power range and transmission range are large, the running noise is small, the efficiency is high, and the service life is long.

As shown in FIGS. 3 to 5, the speed increasing portion 2300 includes a sun gear 2310 disposed at the front end of the rear axle 2200 and then rotating the shaft 2200, and a planetary gear 2320 disposed at the rear end of the front axle 2100 and rotating with the front axle 2100. The teeth of the planet gear 2320 cooperate with the teeth of the sun gear 2310, and the planet gears 2320 rotate about the sun gear 2310. A fixed wheel 2330 is further disposed on the outer side of the planetary gear 2320. The teeth of the fixed wheel 2330 are engaged with the teeth of the planetary gear 2320, and the fixed wheel 2330 is fixed to the inner wall of the casing assembly 1000. When the planetary gear trains cooperate with each other, the fixed wheel 2330 is fixed, and the rotation speed of the sun gear 2310 is greater than the rotation speed of the planetary gear 2320 around the sun gear 2310, thereby achieving the purpose of speed increase. That is, when the compressor is driven by the clutch assembly 4000, the torque is first transmitted to the front axle 2100, and the front axle 2100 rotates and accelerates through the planetary gear train to transmit torque to the rear axle 2200, thereby driving the scroll assembly 3000. . Here, the number of teeth of the planetary gear mechanism gear can be adjusted to obtain a plurality of gear ratios. In order to reduce the impact of impact and load changes, the sun gear 2310, the planet gears 2320 and the fixed wheels 2330 may all be helical gears, so that the transmission is more stable and the load carrying capacity of the gears can be improved.

6 is a schematic structural view of a front axle 2100 in an embodiment of the present disclosure, in which a carrier 2110 is formed at a rear end of the front axle 2100, and the carrier 2110 is evenly disposed with an eccentric pin 2120 at intervals in the circumferential direction. The eccentric pin 2120 faces the rear axle 2200 and the planet gear 2320 is mounted on the eccentric pin 2120. The eccentric pin 2120 can be integrally formed with the carrier 2110 to maintain the compactness of the structure; a through hole corresponding to the eccentric pin 2120 can also be defined on the carrier 2110, and the eccentric pin 2120 is inserted into the through hole through an interference fit, so that The manufacturing difficulty of the carrier 2110 is lowered, and the replaceability of the parts is strong.

As shown in FIGS. 5 to 7, the eccentric pin 2120 can be three, and the force stability of the planetary gear mechanism can be ensured. Accordingly, the number of the planetary gears 2320 is also three. In order to reduce the mass and reduce the moment of inertia, the carrier 2110 may perform a weight reduction process. Specifically, as shown in FIGS. 5 and 7, the carrier 2110 may include a center disk 2111 and protrude radially outward along the center disk 2111. And along the circumferentially spaced mounting plate 2112, the eccentric pin 2120 is disposed on the mounting plate 2112. The outer contour of the center disk 2111 between adjacent mounting disks 2112 may be a concave arc. The outer contour of each mounting plate 2112 may be a convex arc. A rounded transition can be made between the concave arc and the convex arc to avoid stress concentration. In this way, not only can the planetary carrier 2110 achieve the purpose of weight reduction, but also its strength requirements can be met.

As shown in FIG. 3 and FIG. 4, the front end of the rear axle 2200 may be a stepped shaft with a reduced shaft diameter, and the sun gear 2310 is sleeved. At the front end of the rear axle 2200, that is, the small diameter section 2210 of the stepped shaft described above, and the rear end of the sun gear 2310 abuts against the shoulder 2201 of the stepped shaft to position the sun gear 2310.

As shown in FIG. 3, the inside of the casing assembly 1000 is partitioned into a main cavity 1100 and an auxiliary cavity 1200 which are axially distributed by a partition wall 1300 which is sleeved on the rear axle 2200, wherein the barrier wall 1300 is formed in the casing. The inner wall of the assembly 1000 has a stable structure. The auxiliary cavity 1200 is defined between the front end cover 1400 of the cabinet assembly 1000 and the barrier wall 1300. The front axle 2100 is located in the clutch assembly 4000, the speed increasing portion 2300 is located in the auxiliary chamber 1200, and the rear axle 2200 is located in the main chamber 1100. That is, in the present disclosure, the speed increasing portion 2300 is separately disposed in one space, that is, in the auxiliary cavity 1200, by the arrangement of the partition wall 1300, so that the parts of the speed increasing portion are smoothly driven, and are easy to be arranged without being adversely affected by other components. , such as interference in the arrangement space.

In the embodiment using the planetary gear mechanism illustrated in Figures 3 and 4, the main body portion of the front axle 2100 and the main body portion of the rear axle 2200 are mounted in a manner similar to the prior art integrated crankshaft mounting, where no longer Narration. The carrier 2110, the sun gear 2310, the planet wheels 2320, and the fixed wheel 2330 are all disposed in the auxiliary cavity 1200, wherein the rear end of the speed increasing portion 2300 is limited by the above-described stepped shaft shoulder 2201, and the rear end of the fixed wheel 2330 Abutting against the partition wall 1300, the front end of the speed increasing portion 2300 is restrained by the carrier 2110 on the front end cover 1400, thereby maintaining the compactness of the speed increasing portion 2300 in the axial direction, which can be at the crankshaft 2000. When the axial dimension is not increased much, the gear ratio is effectively increased.

Further, to ensure the tightness between the barrier wall 1300 and the crankshaft 2000, a first shaft seal 8001 is disposed between the barrier wall 1300 and the crankshaft 2000, and a gap between the barrier wall 1300 and the crankshaft 2000 is also provided. The first circlip 8002 is axially positioned to the first shaft seal 8001. In the embodiment illustrated in FIGS. 3 and 4, the first shaft seal 8001 and the first snap spring 8002 are disposed between the barrier wall 1300 and the rear axle 2200.

In summary, in the present disclosure, the crankshaft 2000 is set as a split structure, and the speed increasing portion 2300 is added to improve the transmission efficiency, and the transmission ratio is effectively increased and the compressor row is reduced in the case where the axial dimension does not increase much. Quantity requirements. In addition, when the planetary gear mechanism is used as the speed increasing portion, the transmission is stable, and different gear ratios can be designed, which is reliable in operation and high in stability.

Electric drive mode

As shown in FIG. 3, another driving mode of the dual drive compressor provided by the present disclosure is electrically driven by a motor assembly 5000 disposed in the casing assembly 1000, wherein the motor assembly 5000 includes a total positioning of the casing. a stator assembly 5100 having an inner wall of 1000 and a rotor assembly 5200 mounted on the crankshaft 2000, wherein as shown in FIG. 3, the stator assembly 5100 can be positioned by a stepped surface 1001 formed on an inner wall of the casing assembly 1000, the rotor assembly The 5200 drives the crankshaft 1000 to rotate after being energized, thereby driving the scroll assembly 3000 to complete the compression of the refrigerant. Specifically, electricity The control assembly 6000 converts the direct current flowing from the high voltage harness into an alternating current into the stator assembly 5100, and the stator assembly 5100 forms a varying magnetic field. The rotor assembly 5200 located inside the stator assembly 5100 drives the crankshaft 2000 under the action of the magnetic field. Rotate together.

Mode switching between mechanical drive mode and electric drive mode

The motor assembly 5000 does not operate when the compressor is in the mechanical drive mode. When the mechanical drive mode is switched to the electric drive mode, the aforementioned clutch assembly 4000 disconnects the drive line, the pulley stops providing the driving force to the crankshaft 2000, and the electronic control assembly 6000 receives the driving force switching information (specifically, may be from the entire vehicle The controller's coil is powered off, and a start command is issued to the motor assembly 5000 to initiate the electric drive mode. Similarly, when switching from the electric drive mode to the mechanical drive mode, the motor assembly 5000 is stopped, and the information is transmitted to the vehicle controller by the electronic control assembly 6000, and the vehicle controller issues an instruction to enable the mechanical drive mode.

In order to improve the smooth rotation of the crankshaft 2000 during the driving force switching, and to reduce the impact of the rotational speed mismatch on the motor and the clutch assembly, in the present disclosure, the dual drive compressor may include a resolver 7000 mounted on the crankshaft 2000, The resolver 7000 is electrically connected to the electronic control assembly 6000 for transmitting the rotational speed signal of the crankshaft 2000 to the electronic control assembly 6000 or the vehicle controller when the driving mode is switched, so that the mode switching is smooth and the compressor works smoothly. As shown in FIG. 3, since the scroll assembly 3000 is driven by the rear axle 2200, and the rear axle 2200 is formed as the main body of the crankshaft 2000, the resolver 7000 can be mounted on the rear axle 2200, the following resolver 7000 and the crankshaft. The cooperation of 2000 means that the spinning 7000 is matched with the rear axle 2200.

As shown in FIGS. 2, 3, 8, and 9, the resolver 7000 includes a resolver stator 7100, a resolver rotor 7200 mounted on the crankshaft 2000 that is rotatable with the crankshaft 2000, and a connection to the resolver stator 7100. The revolving wire harness 7300 and the revolving wire harness 7300 are electrically connected to the electric control assembly 6000 to realize signal interaction.

A through hole is formed in the casing assembly 1000, and the through hole connects the resolver 7000 and the electronic control assembly 6000, and connects the motor assembly 5000 and the electronic control assembly 6000. In order to avoid interference of the wires with each other, as shown in FIG. 10, a screw-type wiring hole 1002 and a motor wiring hole 1003 are formed in the casing assembly 1000. In addition, when the resolver 7000 is installed, the resolver 7000 is placed close to the motor assembly 5000 such that the resolver 7000 and the motor assembly 5000 are placed in an area within the casing assembly 1000 during wiring to facilitate the lead.

As shown in FIG. 2, the resolver rotor 7200 is sleeved on the crankshaft 2000, and the resolver stator 7100 is formed on the outer circumference of the resolver rotor 7200. The casing assembly 1000 is provided with a support plate 1500 sleeved on the crankshaft 2000. A first stepped surface 1510 is formed on the inner peripheral surface of the disk 1500 to position the resolver stator 7100. As shown in FIG. 2, FIG. 9, and FIG. 11, the first stepped surface 1510 may be formed on the front end surface of the support disk 1500, and the outer periphery of the rotary stator 7100 is provided with a first flange 7110 to be abutted on the first stepped surface 1510. The pick-and-place from the end can make the assembly and disassembly of the spinning assembly 7000 convenient and unnecessary. In the case of moving the support disk 1500, the spinning assembly 7000 is quickly disassembled to improve work efficiency.

Here, the support plate 1500 can be adapted to the specific structural design of the crankshaft 2000. For example, in the embodiment shown in FIGS. 2 and 3, the rear end of the support plate 1500 is recessed to form a hollow region, and the movable plate 3200 and the crankshaft 2000 are The mating portion is disposed in the hollow region to save axial dimension.

As shown in FIG. 11, the support plate 1500 can be mounted on the crankshaft 2000 through the first bearing 8003. The rear end of the first bearing 8003 abuts against the second stepped surface 2001 on the crankshaft 2000 for rear positioning. The first bearing 8003 The front end abuts against the inwardly projecting annular wall 1520 of the support disk 1500 for front positioning.

As shown in FIG. 11, the annular wall 1520 extends radially to the crankshaft 2000, and a second oil seal 8004 is disposed between the annular wall 1520 and the crankshaft 2000 to prevent liquid leakage and is disposed between the annular wall 1520 and the crankshaft 2000. There is a second retaining spring 8005 for axially positioning the second shaft seal 8004. In addition, a circlip spring 8007 sleeved on the crankshaft 2000 may be disposed at the front end surface of the first bearing 8003. The circlip spring 8007 is engaged with the crankshaft 2000 to further limit the first bearing 8003.

Further, as shown in FIGS. 2, 3 and 11, the rear end of the support disk 1500 is formed with a second flange 1530, and the outer periphery of the second flange 1530 abuts against the inner wall of the casing assembly 1000, thereby vortexing The disk assembly 3000 is isolated from the body portion of the crankshaft 2000 to define the aforementioned compression chamber region. As shown in Figures 2, 3 and 11, the second flange 1530 of the support disk 1500 can be secured to the static disk 3100 by a first bolt 8006 to increase the compactness of the device.

The operation of the resolver 7000 will be briefly described below with reference to FIG.

When the dual-drive compressor is in the mechanical drive mode, its speed is determined by the engine speed, and the engine supplies power to the vehicle while working. After the power is sufficient, the electronic control assembly 6000 will receive a command to switch to the electric drive mode, and immediately send a request signal to the dual drive compressor, the coil 4100 is powered off, and the pulley 4300 and the drive plate 4200 are separated.

At the moment of switching, the crankshaft 2000 continues to operate due to inertia. When the motor assembly 5000 receives the start command, it needs to know the spatial phase angle of the rotor assembly 5200 and the stator assembly 5100 to correctly give the starting angle for the stator assembly. Power on the 5100. At this time, the resolver 7000 can read the current rotational speed and spatial angle of the crankshaft 2000 in real time, and feed back to the electronic control assembly 6000. After receiving the information, the electronic control assembly 6000 gives the stator coil of the correct phase of the motor assembly 5000. When the power is turned on, the corresponding starting current and starting angle are input, and the mechanical driving mode to the electric driving mode is switched.

When the dual drive compressor is in the electric drive mode, its speed is determined by the electronic control assembly 6000. When the whole vehicle is feeding, the electronic control assembly 6000 will receive the command to switch to the mechanical drive mode, and immediately send a request signal to the dual drive compressor, the compressor disconnects the high voltage, and the cyclone 7000 reads the current crankshaft 2000. The speed is fed back to the electronic control assembly 6000. The electronic control assembly 6000 reads the engine speed. The engine speed is controlled by the vehicle controller to match the speed of the crankshaft 2000. When the synchronous speed is reached, the coil of the compressor clutch assembly 4000 4100 power on, make pulley 4300 and drive plate The 4200 is engaged to complete the switching from the electric drive mode to the mechanical drive mode. The two drive modes are switched to each other to reduce the impact of the speed mismatch on the compressor and make the operation smoother.

Electronic control assembly

In the dual-drive compressor, the electronic control assembly 6000 is an indispensable component, and the electronic control assembly 6000 is electrically connected to the vehicle controller, and the two drive modes are mutually switched by the signal interaction with the vehicle controller. The electronic control assembly 6000 generally refers to the whole of all electronic components integrated into an electric control box, and also includes the electric control box itself. The connection of the electronic control assembly 6000 mainly involves electrical connection and physical connection, wherein the physical connection is mainly Refers to the connection between the shells.

In one embodiment of the present disclosure, as shown in FIGS. 12 and 13, the electronic control assembly 6000 is detachably mounted outside the casing assembly 1000, and between the electronic control assembly 6000 and the motor assembly 5000. Electrical connection is made via pluggable electrical connectors. That is, in the present embodiment, in the physical connection portion, the electronic control assembly 6000 and the casing assembly 1000 can be disassembled by bolt fastening or the like. As shown in FIG. 12, the outer side of the electronically controlled housing 6100 may be provided with fasteners 8015 at intervals to secure the housing assembly 1000 and the electronic control assembly 6000. The electrical connection can be made via pluggable electrical connectors. In this way, the utility model has the advantages of high interchangeability and convenient disassembly and assembly. When the electronic control assembly 6000 fails, the electronic control housing 6100 only needs to be disassembled and repaired from the compressor, and the main body portion of the compressor is not affected; When the control assembly 6000 fails, it only needs to replace the 6000 part of the electronic control assembly, which saves the after-sales cost.

As shown in FIG. 12, the electronic control assembly 6000 includes an electronically controlled housing 6100 and a control component housed in the electronically controlled housing 6100. The electronically controlled housing 6100 is positively coupled to the outside of the housing assembly 1000, wherein the shape fit refers to The shape of the mating surface of the electronically controlled outer casing 6100 and the casing assembly 1000 correspond to each other, so that the overall structure of the compressor is compact. For example, the thickness of the two side walls of the electronically controlled casing 6100 in FIG. 2 is different, that is, to adapt to the casing. The design made by the shape of the assembly 1000.

As shown in FIG. 12, the electronic control housing 6100 includes a first base 6110 and a first cover 6120. A first sealing gasket is disposed between the first base 6110 and the first cover 6120, and the electronic control housing 6100 is further disposed. The low voltage wiring port 6101 and the high voltage wiring port 6102, the low voltage wiring port 6101 is used for connecting with the vehicle controller, and the high voltage wiring port 6102 is for receiving high voltage power, and then supplying power to the motor assembly 5000.

The electrical connector of the electronic control assembly 6000 may include a three-phase connector 6001. In conjunction with FIG. 13, the electrical connector of the motor assembly 5000 may include a corresponding three-phase terminal 5001, a three-phase terminal 5001 and a three-phase connector 6001. Plug and play connection.

The control element comprises an electronically controlled printed circuit board (PCB). The control circuit is formed on the electronic control PCB. The three-phase connector 6001 is fixedly connected to the electronic control PCB and extends outward through the electronic control housing 6100. Out, for use with the three-phase terminal 5001. Correspondingly, the casing assembly is provided with a motor wiring hole 1003 from which the three-phase terminal 5001 is The motor wiring hole 1003 protrudes for mating with the three-phase connector 6001, and the three-phase connector 6001 and the three-phase terminal 5001 can be connected to the circuit on the PCB electronic control board.

It should be noted that the three-phase terminal 5001 penetrates the outer wall of the casing assembly 1000, and the fixed form thereof can be realized by various embodiments.

In the present disclosure, as shown in FIG. 13, the three-phase terminal 5001 includes a first mounting disk 5001a embedded in the motor wiring hole 1003, and three first pins 5001b inserted in the first mounting disk 5001a. As the main electrical connection component of the three-phase terminal 5001, the stator assembly 5100 in the motor assembly 5000 is connected to the first pin 5001b by twisting. Correspondingly, on the side of the electronic control assembly 6000, the three-phase connector 6001 includes a first female terminal 6001a that can wrap the first pin 5001b in an interference fit, and the first female terminal 6001a can be soldered through the first pin 6001b. On the electronic control PCB.

Further, a third stepped surface 1003a is formed on the motor connecting hole 1003. One end of the first mounting plate 5001a abuts on the third stepped surface 1003a, and the other end passes through a third circlip spring 8008 fixed on the casing assembly 1000. The third retaining spring 8008 is disposed in an interference fit on the inner wall of the motor wiring hole 1003. Further, a first first mounting disc 5001a and the motor wiring hole 1003 may be disposed first. Seal 8009 to prevent leakage of liquid. In the plugged state, a second sealing ring 8010 is disposed between the electronically controlled housing 6100 and the housing assembly 1000 corresponding to the motor wiring hole 1003 to prevent external moisture from entering and affecting electrical performance.

To prevent current on the first pin 5001b from flowing to the chassis assembly 1000 or other components, a first sleeve disposed on the first pin 5001b is disposed between the first pin 5001b and the first mounting pad 5001a. The insulator 5001c; a portion of the first lead 5001b protruding from the first mounting plate 5001a is sleeved with a second insulator 5001d; and a portion of the first pin 5001b inserted into the casing assembly 1000 is sleeved with a third insulator 5001e. Each of the first insulator 5001c, the second insulator 5001d, and the third insulator 5001e may be made of a material such as glass, ceramic, or silica gel.

In addition, as shown in FIG. 12, the outer side of the electronically controlled housing 6100 corresponds to the position of the low pressure chamber of the dual drive compressor covered with the layer of thermally conductive material 8011, that is, the position of the first base 6110 in contact with the cabinet assembly 1000. Covered with a layer of thermal conductive material 8011, the electronic control assembly 6000 is used for rapid heat dissipation, improving work efficiency and prolonging service life. It should be noted that the working chamber of the compressor includes a compression chamber at the working portion of the scroll assembly 3000, a back pressure chamber in the direction of the air inlet, and a high pressure chamber in the direction of the air outlet. The low pressure chamber is different from the compression. The cavity, the back pressure chamber and the high pressure chamber, the low pressure chamber is mainly formed in the main body region of the crankshaft 2000, which is the region where most of the components of the compressor are located, and the low temperature and low pressure refrigerant in the low pressure chamber flows through the casing assembly 1000, Allow the electronic control assembly 6000 to dissipate heat.

In addition, after the cyclone 7000 is set in the dual-drive compressor, the electrical control assembly 6000 and the revolving 7000 are also electrically connected through a pluggable electrical connector in a form similar to the electronic control assembly 6000 and the motor assembly. The connection of 5000, as shown in FIG. 12, is provided with a revolving connector 6002 on the electronic control PCB, and the revolving connector 6002 passes through the electronically controlled housing 6100. The splicing terminal 7001 led out from the resolver harness 7300 is coupled to the following. Correspondingly, the casing assembly 1000 is provided with a spinning terminal 1002 through which the spinning terminal 7001 passes to be inserted and removed with the above-mentioned splicing connector 6002.

The revolving terminal 7001 extends through the outer wall of the casing assembly 1000, and its fixed form can be realized by various embodiments. In the present disclosure, as shown in FIG. 15 and FIG. 16a, the revolving terminal 7001 includes an in-line revolving The second mounting disk 7001a in the wiring hole 1002 is inserted into the second pin 7001b in the second mounting disk 7001a, and the second pin 7001b is electrically connected to the revolving wire harness 7300, and the spinning connector 6002 and the chassis are always connected. The features are matched and angularly oriented. The structure of the resolver connector 6002 is as shown in Fig. 16b: the second female terminal 6002a is positioned by the grip on the sheath 6002d, and the end of the second female terminal 6002a is connected by riveting the second pin 6002b or by a twisted wire. The electronic control PCB board is fixed by the sealing body 6002e, and is axially positioned by the back cover 6002f having the error-proof feature, wherein the second pin 6002b can be soldered to the electronic control PCB. The front cover 6002c of the resolver connector 6002 has a circular feature, and the front cover 6002c covers and fixes the front portion of the second female terminal 6002a for guiding and fixing. The second female terminal 6002a can wrap the second pin 7001b with an interference fit. Thus, after the spinning terminal 7001 and the rotating connector 6002 are plugged in, the spinning harness 7300 can be connected to the circuit of the electronic control PCB. In addition, a mating connector is further disposed on the casing assembly 1000. The mating connector and the revolving connector 6002 are substantially symmetrical with respect to the second mounting disc 7001a, and the mating connector and the revolving connector are matched. The structure of the 6002 is the same, and the two ends of the second pin 7001b are respectively connected to the splicing connector 6002 and the mating connector. The resolver harness 7300 is connected to the mating connector by means of a twisted wire.

Further, a fourth stepped surface 1002a is formed on the slewing wiring hole 1002. One end of the second mounting disk 7001a abuts on the fourth stepped surface 1002a, and the other end passes through a fourth card fixed on the casing assembly 1000. Spring 8012 limit. As shown in FIGS. 15 and 16a, the fourth catcher spring 8012 is disposed in an interference fit on the inner wall of the resolver wire hole 1002. In addition, a third sealing ring 8013 may be disposed between the second mounting plate 7001a and the rotating wiring hole 1002 to prevent liquid leakage. In the plugged state, a fourth sealing ring 8014 is disposed between the electronically controlled housing 6100 and the housing assembly 1000 corresponding to the position of the rotating wiring hole 1002 to prevent external moisture from entering and affecting electrical performance. The shoulder 6002g of the mating connector is abutted against the fifth stepped surface 1002b of the casing assembly 1000 to further position the mating connector and prevent the component from falling into the interior of the casing assembly 1000.

To prevent current on the second pin 7001b from flowing to the chassis assembly 1000 or other components, a fourth sleeve disposed on the second pin 7001b is disposed between the first pin 7001b and the second mounting pad 7001a. The insulator 7001c and the fourth insulator 7001c may be made of a material such as glass, ceramic or silica gel.

The preferred embodiments of the present disclosure have been described in detail above with reference to the accompanying drawings. However, the present disclosure is not limited to the specific details of the above embodiments, and various simple modifications can be made to the technical solutions of the present disclosure within the scope of the technical idea of the present disclosure. These simple variations are all within the scope of the disclosure.

It should be further noted that the specific technical features described in the above specific embodiments may be combined in any suitable manner without contradiction. In order to avoid unnecessary repetition, the present disclosure is applicable to various possibilities. The combination method will not be described separately.

In addition, any combination of various embodiments of the present disclosure may be made as long as it does not deviate from the idea of the present disclosure, and should also be regarded as the disclosure of the present disclosure.

Claims

A dual drive compressor comprising a casing assembly (1000), a scroll assembly (3000), a crankshaft (2000) and a motor assembly (5000) located inside the casing assembly (1000), mounted on An electronic control assembly (6000) external to the housing assembly (1000), and a clutch assembly (4000) coupled to the crankshaft (2000), characterized in that the electronic control assembly (6000) is detachable The ground is mounted on the outside of the casing assembly (1000), and the electrical control assembly (6000) and the motor assembly (5000) are electrically connected by a pluggable electrical connector.
The dual drive compressor of claim 1 wherein said electronic control assembly (6000) includes an electrically controlled housing (6100) and a control element housed in said electrically controlled housing (6100), said An electrically controlled housing (6100) is positively coupled to the outside of the housing assembly (1000).
The dual drive compressor according to claim 2, wherein the electrical connector of the electronic control assembly (6000) comprises a three-phase connector (6001), and the electrical connector of the motor assembly (5000) comprises A three-phase terminal (5001), the three-phase terminal (5001) is pluggably connected to the three-phase connector (6001).
The dual drive compressor of claim 3 wherein said control element comprises an electrically controlled printed circuit board (PCB) board, said three phase plug (6001) being coupled to said electronically controlled PCB And extending outward through the electronically controlled housing (6100).
The dual drive compressor according to claim 4, wherein the casing assembly is provided with a motor wiring hole (1003), and the three-phase terminal (5001) is from the motor wiring hole (1003). Extendingly, the three-phase terminal (5001) is electrically connected to the motor assembly (5000).
A dual drive compressor according to claim 5, wherein said three-phase terminal (5001) includes a first mounting plate (5001a) embedded in said motor wiring hole (1300), plugged in a pin (5001b) in the first mounting disk (5001a), the pin (5001b) is electrically connected to the motor assembly (5000), and the three-phase connector (6001) includes an interference The female terminal (6001a) of the pin (5001b) is cooperatively wrapped, and the female terminal (6001a) is fixedly connected to the electronic control PCB through a pin (6001b).
The dual drive compressor according to claim 6, wherein a stepped surface (1003a) is formed on the motor wiring hole (1003), and one end of the first mounting disk (5001a) abuts against the step On the face (1003a), the other end is limited by a snap spring (8008) fixed to the casing assembly (1000).
The dual drive compressor according to claim 6, wherein a first seal ring (8009) is disposed between the first mounting plate (5001a) and the motor wiring hole (1003).
The dual drive compressor according to claim 6, wherein a first insulator sleeved on the pin (5001b) is disposed between the pin (5001b) and the first mounting plate (5001a) (5001c).
The dual drive compressor according to claim 6, wherein a portion of the lead (5001b) extending from the first mounting plate (5001a) is sleeved with a second insulator (5001d).
The dual drive compressor according to claim 6, wherein a portion of the lead (5001b) inserted into the casing assembly (1000) is sleeved with a third insulator (5001e).
The dual drive compressor according to claim 2, wherein the outer side of the electronically controlled casing (6100) is provided with fasteners (8015) spaced apart to fix the casing assembly (1000) and electricity. Control assembly (6000).
The dual drive compressor of claim 2, wherein the electronically controlled housing (6100) includes a base (6110) and a cover plate (6120), between the base (6110) and the cover plate (6120) A gasket (6130) is provided, and the electronic control housing (6100) is further provided with a low voltage wiring port (6101) and a high voltage wiring port (6102).
A dual drive compressor according to claim 2, wherein the outer side of said electronically controlled housing (6100) is covered with a layer of thermally conductive material (8011) corresponding to the location of the low pressure chamber of said dual drive compressor.
The dual drive compressor according to claim 2, wherein in the plugged state, the electric control housing (6100) and the housing assembly (1000) correspond to the motor wiring hole (1003) The position is provided with a second sealing ring (8010).
A dual drive compressor according to any one of claims 1 to 14, wherein said crankshaft (2000) comprises a coaxially coupled front axle (2100) and a rear axle (2200), said front axle ( A speed increasing portion (2300) is provided between the 2100) and the rear axle (2200) such that the rotational speed of the rear axle (2200) is greater than the rotational speed of the front axle (2100).
The dual drive compressor according to claim 15, wherein said speed increasing portion (2300) is a planetary gear mechanism.
The dual drive compressor according to claim 16, wherein said speed increasing portion (2300) includes a sun gear disposed at a front end of said rear axle (2200) and rotating with said rear axle (2200) ( 2310), a planet gear (2320) disposed at a rear end of the front axle (2100) and rotating with the front axle (2100), teeth of the planet gear (2320) and the sun gear (2310) The teeth cooperate, and the planetary gear (2320) rotates around the sun gear (2310), and the outer side of the planetary gear (2320) is further provided with a fixed wheel (2330), the teeth of the fixed wheel (2330) The planet gear (2320) is a toothed engagement fixed wheel (2330) that is fixed to the inner wall of the casing assembly (1000).
The dual drive compressor according to claim 17, wherein a rear end of the front axle (2100) is formed with a carrier (2110), and the carrier (2110) is evenly arranged with an eccentricity at intervals in the circumferential direction. A pin (2120) on which the planet gear (2320) is mounted.
The dual drive compressor according to claim 18, wherein said carrier (2110) comprises a center disk (2111), and protrudes outward in a radial direction of said center disk (2111) and along the circumference Second installation to the interval A disk (2112), the eccentric pin (2120) being disposed on the second mounting plate (2112).
The dual drive compressor according to claim 15, wherein the inside of the casing assembly (1000) is divided into axial directions by a partition wall (1300) sleeved on the crankshaft (2000) a distributed main cavity (1100) and an auxiliary cavity (1200), the auxiliary cavity (1200) being defined between the front end cover (1400) of the casing assembly (1000) and the barrier wall (1300), The front axle (2100) is located in the clutch assembly (4000), the speed increasing portion (2300) is located in the auxiliary cavity (1200), and the rear axle (2200) is located in the main cavity (1100) )in.