CN114789643A

CN114789643A - Vehicle-mounted air conditioner and automobile

Info

Publication number: CN114789643A
Application number: CN202210472725.5A
Authority: CN
Inventors: 谭长伟; 何金平
Original assignee: Chongqing Jinkang Sailisi New Energy Automobile Design Institute Co Ltd
Current assignee: Chongqing Jinkang Sailisi New Energy Automobile Design Institute Co Ltd
Priority date: 2022-04-29
Filing date: 2022-04-29
Publication date: 2022-07-26
Anticipated expiration: 2042-04-29
Also published as: CN114789643B

Abstract

The application relates to a vehicle-mounted air conditioner and an automobile, wherein the vehicle-mounted air conditioner comprises: the top of the shell is provided with an air inlet mechanism; the partition plate is horizontally arranged in the shell and divides the inner space of the shell into a front-row channel and a rear-row channel, the shell is provided with a front air outlet at the front-row channel, and the shell is provided with a rear air outlet at the rear-row channel; and the adjusting mechanism comprises a front evaporator and a rear evaporator, the rear evaporator is configured with an operating state and a non-operating state, the front evaporator is vertical to the partition plate, one end of the front evaporator extends to the partition plate, and the other end of the front evaporator extends to the maximum height position of the front air outlet. The application provides a vehicle-mounted air conditioner improves the refrigerated effect of vehicle-mounted air conditioner through reducing air resistance, reinforcing heat exchange efficiency and reducing energy loss matched with mode when only refrigerating the front row of car to the inside rapid cooling to the car, and then reinforcing passenger's experience is felt.

Description

Vehicle-mounted air conditioner and automobile

Technical Field

The application relates to the technical field of automobiles, in particular to an on-vehicle air conditioner and an automobile.

Background

An HVAC (Heating Ventilation and Air Conditioning) system may be used in an automobile, that is, to form an "on-board Air conditioner" for adjusting environmental parameters such as temperature and humidity inside the automobile.

Vehicle air conditioners generally include an evaporator for cooling an air stream to cool the interior of an automobile. In the prior art, a vehicle-mounted air conditioner can adopt double evaporators to respectively cool front-row and rear-row airflows of an automobile, and at least one evaporator has two states of working and non-working, so that only one evaporator is started to cool the front-row airflow of the automobile when no passenger is in the rear row of the automobile, and the purpose of saving energy is further achieved.

However, when the vehicle-mounted air conditioner in the prior art only uses one evaporator to cool the front-row airflow of the automobile, the temperature reduction inside the automobile is slow, and the experience of passengers is poor.

Disclosure of Invention

Based on this, this application provides a vehicle-mounted air conditioner and car to the slow problem of inside cooling of car when only adopting an evaporimeter is improved vehicle-mounted air conditioner among the prior art.

In a first aspect, the present application provides a vehicle air conditioner, comprising:

the air inlet mechanism is arranged at the top of the shell and used for sending airflow into the shell;

the partition plate is horizontally arranged in the shell and divides the inner space of the shell into a front row channel at the upper position and a rear row channel at the lower position, a front exhaust port is formed in the front row channel of the shell and used for enabling the airflow to enter the front row of the automobile, and a rear exhaust port is formed in the rear row channel of the shell and used for enabling the airflow to enter the rear row of the automobile;

and the adjusting mechanism comprises a front evaporator and a rear evaporator which are respectively arranged in the front row channel and the rear row channel, the rear evaporator is configured with two states of working and non-working, the front evaporator is vertical to the partition plate, one end of the front evaporator extends to the partition plate, and the other end of the front evaporator extends to the maximum height position of the front exhaust port.

In one embodiment, the adjusting mechanism further comprises a warm air core, one part of which is arranged in the front row of the channels and the other part of which is arranged in the rear row of the channels, for heating the air flow, the warm air core being arranged in parallel with the front evaporator.

In one of them embodiment, be provided with the floor in the casing, the floor level set up in the front row passageway, one side of floor with the warm braw core is located one end butt in the front row passageway, and will the front row passageway is separated and is close to the warm braw passageway of division board and keep away from the cold wind passageway of division board, still rotate in the casing and be provided with warm braw front damper and mix the air door, warm braw front damper with mix the air door and rotate to the level in order respectively with the warm braw passageway with the cold wind passageway is opened to rotate to vertical in order respectively with the warm braw passageway with the cold wind passageway is closed.

In one embodiment, the front exhaust air outlet comprises an upper front blowing surface air outlet and a lower front foot blowing air outlet, the height position of the rotating shaft of the mixing air door for rotation is smaller than the maximum height position of the front blowing surface air outlet, and the height position of the rotating shaft of the warm air front air door for rotation is smaller than the maximum height position of the front foot blowing air outlet.

In one embodiment, a warm air rear air door is further rotatably arranged in the shell, the warm air rear air door is arranged at one end, away from the warm air front air door, of the rib plate, the warm air rear air door rotates to be vertical to seal the part, located in the front row of channels, of the warm air core body, and rotates to be horizontal to keep the open state of the warm air channels.

In one embodiment, guide plates are arranged at two ends of each rib plate, the guide plates extend in a flaring mode in the direction close to the partition plates, and the warm air front air door and the warm air rear air door are respectively abutted to one partition plate when rotating to be vertical.

In one embodiment, the partition plate is perpendicular to a cross section of the front evaporator in the flow direction of the airflow.

In one embodiment, the front evaporator has a volume greater than the volume of the rear evaporator.

In one embodiment, the cross-sectional area of the front evaporator in the flow direction of the airflow is larger than the cross-sectional area of the rear evaporator in the flow direction of the airflow.

In a second aspect, the present application provides an automobile comprising the in-vehicle air conditioner provided in the application.

The application provides a vehicle-mounted air conditioner improves the cryogenic effect of vehicle-mounted air conditioner through reducing air resistance, reinforcing heat exchange efficiency and reducing loss of energy matched with mode when only refrigerating the front bank of car to inside rapid cooling to the car, and then reinforcing passenger's experience is felt.

Drawings

Fig. 1 is a schematic structural diagram of a vehicle-mounted air conditioner according to an embodiment of the present application;

fig. 2 is a schematic view illustrating a vehicle-mounted air conditioner refrigerating a front row according to an embodiment of the present application;

fig. 3 is a schematic structural diagram of an adjusting mechanism of a vehicle air conditioner according to an embodiment of the present application;

fig. 4 is a schematic view illustrating a vehicle-mounted air conditioner heating a front row according to an embodiment of the present application;

fig. 5 is another schematic diagram of a vehicle air conditioner according to an embodiment of the present application when heating a front row.

Reference numerals are as follows: 1. a housing; 11. a front row of channels; 111. a warm air channel; 112. a cold air passage; 12. a back row channel; 13. a rib plate; 14. a guide plate; 2. an air intake mechanism; 3. a partition plate; 4. a front exhaust port; 41. a front blowing surface tuyere; 42. a front blowing foot air port; 43. a front air door; 44. a rib plate; 5. a rear air outlet; 6. an adjustment mechanism; 61. a front evaporator; 62. a rear evaporator; 63. a warm air core body; 631. a heat source inlet pipe; 632. a heat source outlet pipe; 64. a cold source inlet pipe; 65. a cold source outlet pipe; 66. an inlet manifold; 67. an outlet manifold; 68. a throttle valve; 71. a warm air front air door; 72. a mixing damper; 73. a warm air rear air door; 8. defrosting the tuyere; 81. a defrosting air door; 811. a first side surface; 812. a second side.

Detailed Description

In order to make the objects, technical solutions and advantages of the present application more clearly understood, the present application is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of and not restrictive on the broad application.

It should be noted that the illustrations provided in the present embodiments are only schematic illustrations of the basic idea of the present invention.

The structures, proportions, and dimensions shown in the drawings and described in the specification are for illustrative purposes only and are not intended to limit the scope of the present invention, which is defined by the following claims.

References in this specification to orientations or positional relationships such as "upper," "lower," "left," "right," "middle," "longitudinal," "lateral," "horizontal," "inner," "outer," "radial," "circumferential," and the like are based on the orientations or positional relationships illustrated in the drawings and are intended to simplify the description, rather than to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are not to be construed as limiting the invention. Furthermore, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

As shown in fig. 1 and 2, the present application discloses a vehicle air conditioner including:

a housing 1 which is hollow and provided with an air inlet mechanism 2 at the top for sending airflow into the housing 1;

the partition plate 3 is horizontally arranged in the shell 1 and divides the inner space of the shell 1 into a front row channel 11 at the upper position and a rear row channel 12 at the lower position, a front exhaust port 4 is arranged at the front row channel 11 of the shell 1 and used for allowing airflow to enter the front row of the automobile, and a rear exhaust port 5 is arranged at the rear row channel 12 of the shell 1 and used for allowing airflow to enter the rear row of the automobile; and

the adjusting mechanism 6, the adjusting mechanism 6 includes front evaporator 61 and back evaporator 62 set in front row channel 11 and back row channel 12 separately, the back evaporator 62 is disposed with two states of working and not working, the front evaporator 61 is perpendicular to the divider 3, and one end of the front evaporator 61 extends to the divider 3, another end extends to the maximum height position of the front exhaust vent 4.

In the present embodiment, the intake mechanism 2 adopts a forced induction type, which is exemplarily described. The partition plate 3 is disposed in the casing 1 in a non-penetrating manner, and extends horizontally from one end of the casing 1 far away from the air intake mechanism 2 to one end of the casing 1 close to the air intake mechanism 2, in other words, one end of the partition plate 3 close to the air intake mechanism 2 is not connected to a side wall of the casing 1, so that an air flow sent into the casing 1 by the air intake mechanism 2 can flow along two sides of the partition plate 3 at the same time, and then respectively enters the front row of channels 11 and the rear row of channels 12.

The front evaporator 61 and the rear evaporator 62 are perpendicular to the partition plate 3, and the front evaporator 61 and the rear evaporator 62 are disposed at the same position of the partition plate 3, in which case the front evaporator 61 and the rear evaporator 62 are located at both sides of the partition plate 3. Cold sources circulate in the front evaporator 61 and the rear evaporator 62, for example, the front evaporator 61 and the rear evaporator 62 are both communicated with the compressor, and the cold sources are refrigerant of the compressor.

As shown in fig. 2 and 3, specifically, the front evaporator 61 and the rear evaporator 62 are each provided with a cold source inlet pipe 64 and a cold source outlet pipe 65, the cold source inlet pipe 64 is used for the cold source to enter the front evaporator 61 or the rear evaporator 62, and the cold source outlet pipe 65 is used for the cold source to be discharged from the front evaporator 61 and the rear evaporator 62. Furthermore, the cold source inlet pipes 64 of the front evaporator 61 and the rear evaporator 62 are connected, for example, two cold source inlet pipes 64 are provided with an inlet manifold 66 for communicating with the outlet of the compressor; similarly, the cold source outlet pipes 65 of the front evaporator 61 and the rear evaporator 62 are also provided with an outlet manifold 67 for connecting the two cold source outlet pipes 65 and for communicating with the inlet of the compressor. When the cold source circulates in the front evaporator 61 and the rear evaporator 62, heat exchange can be performed on the air flows passing through the front evaporator 61 and the rear evaporator 62, so as to achieve the purpose of cooling the air flows in the front row of channels 11 and the rear row of channels 12, respectively.

The configuration of the rear evaporator 62 with both active and inactive states can be achieved by the following structure: the cool source inlet pipe 64 of the rear evaporator 62 is provided with a throttling valve 68 for controlling a communication state between the cool source inlet pipe 64 of the rear evaporator 62 and the inlet manifold 66. It will be appreciated that when the throttle valve 68 is opened and the cool source inlet pipe 64 of the rear evaporator 62 is connected to the inlet manifold 66, the cool source can be circulated into the rear evaporator 62, which is a state in which the rear evaporator 62 is operated; when the throttle valve 68 is closed, the cool source cannot enter the rear evaporator 62, and it enters the front evaporator 61 only through the cool source inlet pipe 64 of the front evaporator 61, which is a non-operating state of the rear evaporator 62.

Of course, in some embodiments, the front evaporator 61 and the rear evaporator 62 may be in communication with one compressor and the two compressors may be controlled independently for the purpose of configuring the rear evaporator 62 to be in both an active state and an inactive state.

As shown in fig. 2 and 3, when there are passengers in both the front and rear rows of the automobile, the throttle valve 68 is opened, the cold source can enter the front evaporator 61 and the rear evaporator 62 at the same time to cool the air flows passing through the front and rear rows of the

passage

11 and 12, respectively, and the two air flows finally flow to the front and rear rows of the automobile through the front and rear air outlets 4 and 5, respectively, to achieve the purpose of cooling both the front and rear rows of the automobile; when the automobile only has passengers on the front row and no passengers on the rear row, the throttle valve 68 is closed, the rear evaporator 62 does not work, and the cold source only enters the front evaporator 61, so that the vehicle-mounted air conditioner only refrigerates the front row of the automobile, and the waste of energy is avoided.

Because the partition plate 3 is horizontally arranged and the partition plate 3 is vertical to the front evaporator 61, when the partition plate 3 guides the airflow in the front row channel 11, the part of the airflow passes through the front evaporator 61, the air resistance can be reduced in the heat exchange process, and meanwhile, the heat exchange efficiency can be enhanced, so that the aim of obtaining a better refrigeration effect by using limited energy is fulfilled; and because the front evaporator 61 of the present application extends to the maximum height position of the front exhaust opening 4 from the end of the partition plate 3, the number of times of turning can be reduced, and the air flows from the front exhaust opening 4 to the front row of the automobile in a shorter path, so as to achieve the purpose of reducing the energy loss of the air flow in the circulation process. To sum up, this application improves the refrigerated effect of on-vehicle air conditioner through reducing air resistance, reinforcing heat exchange efficiency and reducing energy loss matched with mode when only refrigerating the front bank of car to the inside rapid cooling to the car, and then reinforcing passenger's experience sense.

As shown in fig. 2 and 3, the adjusting mechanism 6 further includes a warm air core 63, a part of which is disposed in the front row passage 11 and another part of which is disposed in the rear row passage 12, for heating the air flow, the warm air core 63 being disposed in parallel with the front evaporator 61.

In the present embodiment, it is exemplarily explained that the warm air core 63 is provided through the partition plate 3, and the partition plate 3 is provided at an intermediate position of the warm air core 63. The warm air core 63 has a heat source circulating therein, for example, the warm air core 63 is communicated with a cooling water tank of an engine of an automobile, and the heat source is cooling water after cooling the engine.

Specifically, the warm air core 63 is provided with a heat source inlet pipe 631 and a heat source outlet pipe 632 for respectively introducing and discharging a heat source into and from the warm air core 63. When the engine of the automobile is running, the cooling water is heated and heated, and the cooling water is conveyed to the warm air core 63 to heat the air flow flowing through the warm air core 63. It can be understood that the portions of the warm air core 63 located in the front row of channels 11 and the rear row of channels 12 can heat the air flow in the front row of channels 11 and the rear row of channels 12 respectively, so as to achieve the purpose of heating the front row and the rear row of the automobile respectively.

As shown in fig. 2, since the warm air core 63 and the front evaporator 61 of the present embodiment are arranged in parallel, the included angle area between the warm air core 63 and the partition plate 3 is a right angle; compared with the vehicle-mounted air conditioning structure with the warm air core 63 obliquely arranged and the acute angle region between the warm air core 63 and the partition plate 3, when the air flow flows through the right angle region, vortex is not easy to form due to the guiding of the warm air core 63, so that the obstruction of the air flow in the flowing process is reduced, and the energy loss of the air flow is reduced. When the vehicle-mounted air conditioner independently refrigerates the front row of the automobile, the arrangement mode can accelerate the cooling speed of the interior of the automobile.

As shown in fig. 2 and 4, a rib plate 13 is provided in the housing 1, the rib plate 13 is horizontally provided in the front row passage 11, one side of the rib plate 13 abuts against one end of the warm air core 63 located in the front row passage 11 and divides the front row passage 11 into a warm air passage 111 close to the partition plate 3 and a cool air passage 112 far from the partition plate 3, a warm air front damper 71 and a mix damper 72 are further rotatably provided in the housing 1, the warm air front damper 71 and the mix damper 72 rotate to be horizontal to respectively open the warm air passage 111 and the cool air passage 112, and rotate to be vertical to respectively close the warm air passage 111 and the cool air passage 112.

In the present embodiment, it is exemplarily explained that the length of the rib 13 is greater than the length of the warm air core 63 in the flow direction of the air current, which is used for guiding the flow of the air current. It is understood that when the air flow passes through the warm air passage 111 near the warm air core 63, the air flow is heated by passing through the warm air core 63; when the air flow passes through the cool air passage 112 away from the warm air core 63, the air flow is not heated. The warm air front damper 71 and the mixing damper 72 are rotatably disposed in the housing 1 by a rotating shaft and are used to control the air flow to the warm air passage 111 or the cool air passage 112, respectively.

As shown in fig. 4, it can be understood that the warm air front damper 71 is opened, the mixing damper 72 is closed, and the air flows to the warm air passage 111, if the air flow is not cooled by the front evaporator 61 before that, this is the heating mode of the vehicle air conditioner; if the air flow is cooled by the front evaporator 61, the vehicle-mounted air conditioner is in the dehumidification heating mode.

As shown in fig. 2, it can be further understood that the warm air front damper 71 is closed, the mixing damper 72 is opened, and the air flow flows to the cool air passage 112, and if before the air flow is cooled by the front evaporator 61, this is the cooling mode of the vehicle air conditioner; if the air flow is not cooled down, the air flow is in an external circulation mode of the vehicle-mounted air conditioner.

More specifically, the rib 13, the warm air front damper 71 and the mixing damper 72 are all symmetrically arranged in the rear row passage 12 along the partition plate 3, at this time, the rib 13 is used for dividing the partition plate 3 of the rear row passage 12 into a warm air passage 111 close to the partition plate 3 and a cool air passage 112 far from the partition plate 3, and the warm air front damper 71 and the mixing damper 72 are used for respectively controlling the opening and closing of the warm air passage 111 and the cool air passage 112 in the rear row passage 12.

Because the warm air front air door 71 and the mixing air door 72 in the embodiment are perpendicular to the partition plate 3 when closed, the included angle areas between the warm air front air door 71 and the partition plate 3 and between the mixing air door 72 and the rib plate 13 are also right angles, and the airflow is not easy to generate vortex in the areas; and because the warm air front damper 71 and the mixing damper 72 are parallel to the partition plate 3 when being opened, when the airflow passes through the warm air front damper 71 and the mixing damper 72, the warm air front damper 71 and the mixing damper 72 can guide the airflow and reduce the resistance of the airflow in the flowing process. In summary, the positions of the warm air front damper 71 and the mixing damper 72 when they are closed and opened can achieve the purpose of reducing air resistance and reducing energy loss of the air flow. When the vehicle-mounted air conditioner independently refrigerates the front row of the automobile, the arrangement mode can enhance the refrigerating effect of the vehicle-mounted air conditioner.

As shown in fig. 2 and 4, the front exhaust vent 4 includes a front blowing surface vent 41 located at the upper side and a front foot blowing vent 42 located at the lower side, the height position of the rotating shaft for the mixing damper 72 to rotate is smaller than the maximum height position of the front blowing surface vent 41, and the height position of the rotating shaft for the warm air front damper 71 to rotate is smaller than the maximum height position of the front foot blowing vent 42.

In the present embodiment, it is exemplarily explained that the front blowing surface tuyere 41 and the front blowing foot tuyere 42 are both arranged at one end of the housing 1 away from the air intake mechanism 2, the front blowing surface tuyere 41 is obliquely arranged in a direction away from the partition plate 3, the extending direction of the front blowing surface tuyere 41 is the flowing direction of the air flow, and the front blowing foot tuyere 42 is arranged in parallel with the partition plate 3, and the extending direction of the front blowing foot tuyere 42 is perpendicular to the flowing direction of the air flow.

More specifically, the casing 1 is provided with a rib plate 44 at a connection position of the front blowing foot tuyere 42 and the front blowing face tuyere 41, for separating the front blowing face tuyere 41 and the front blowing foot tuyere 42, and a height position of the rib plate 44 is smaller than a height position of the rib plate 13. The front blowing surface air opening 41 and the front blowing foot air opening 42 are both rotatably provided with front air doors 43 for controlling the opening and closing of the front blowing surface air opening 41 and the front blowing foot air opening 42, and passengers can control the two front air doors 43 according to actual needs so that air flow is discharged from the front blowing surface air opening 41 and/or the front blowing foot air opening 42.

The cold flow cools the human body from top to bottom in a face blowing mode, and the hot flow heats the human body from bottom to top in a foot blowing mode, so that the human body has strong comfort and the cooling or heating speed is high.

Based on this, as shown in fig. 2, when the front damper 43 at both the front blowing face tuyere 41 and the front foot-blowing tuyere 42 is opened, since the height position of the rotary shaft of the blend door 72 for its rotation is smaller than the maximum height position of the foot-blowing damper, the height position of the blend door 72 is smaller than the maximum height position of the front blowing face tuyere 41 when the blend door 72 is opened and kept horizontal; most of the cold flow passing through the cold air channel 112 of the front exhaust channel 11 can be discharged directly from the front blowing surface tuyere 41 in a horizontal flow manner and used for blowing the front row of the automobile to blow the surface, and the rest of the cold flow is diverted and flows to the front foot blowing tuyere 42 from below the rib plate 44 and used for blowing the front row of the automobile to blow feet.

As shown in fig. 4, since the height position of the rotating shaft of the warm air front damper 71 for rotation is smaller than the maximum height position of the front foot-blowing air inlet 42, when the warm air front damper 71 is opened and kept horizontal, the height position of the warm air front damper 71 is smaller than the maximum height position of the front foot-blowing air inlet 42, most of the heat flow passing through the warm air passage 111 of the front exhaust passage 11 can be directly discharged from the front foot-blowing air inlet 42 in a water flow manner, and the rest of the heat flow is diverted and flows from above the rib plate 44 to the front face-blowing air inlet 41.

In summary, the arrangement manner that the height position of the rotating shaft of the air mixing door 72 is smaller than the maximum height position of the front blowing surface air opening 41 can enhance the refrigeration effect of the vehicle-mounted air conditioner, so that when the vehicle-mounted air conditioner is used for refrigerating the front row of the automobile alone, the interior of the automobile is cooled rapidly. It can also be deduced in the same way that the arrangement mode that the height position of the rotating shaft of the warm air front air door 71 for rotating is smaller than the maximum height position of the front foot blowing air inlet 42 can enhance the heating effect of the vehicle-mounted air conditioner.

As shown in fig. 2 and 4, a warm air rear damper 73 is further rotatably disposed in the housing 1, the warm air rear damper 73 is disposed at an end of the rib 13 away from the warm air front damper 71, and the warm air rear damper 73 is rotated to be vertical to close a portion of the warm air core 63 located in the front row passage 11, and is rotated to be horizontal to maintain an open state of the warm air passage 111.

In the present embodiment, it is exemplarily illustrated that the warm air rear damper 73 and the warm air front damper 71 adopt the same structure, and they are matched with the warm air front damper 71 and the rib 13 in the front row channel 11 to seal the warm air core 63, so as to reduce heat exchange and heat energy radiation between the cold flow and the warm air core 63 when the vehicle-mounted air conditioner is cooling, so as to ensure the cooling effect of the vehicle-mounted air conditioner. It is understood that the warm air rear damper 73 may also be symmetrically disposed in the rear row passage 12 along the partition plate 3.

As shown in fig. 2 and 4, the two ends of the rib 13 are each provided with a guide plate 14, the guide plates 14 extend in a flared manner in a direction close to one side of the warm air passage 111, and the warm air front damper 71 and the warm air rear damper 73 are respectively abutted against one guide plate 14 when rotated to be vertical.

In the present embodiment, it is exemplarily illustrated that the guide plate 14 is integrally formed with the rib 13, and the connection is in a rounded transition. The two guide plates 14 may be both obliquely arranged and symmetrically arranged along the axial cross section in the middle of the length direction of the rib plate 13 to form the flare, and the guide plates 14 extend to positions abutting against the warm air front damper 71 and the warm air rear damper 73 when closed. The guide plate 14 is used for connecting the rib plate 13 and the warm air front damper 71 and the warm air rear damper 73 when closed, so that a chamfer-shaped structure is formed at the connection part, and the guide plate guides the flow of the air flow, thereby reducing the resistance of the air flow.

As shown in fig. 2 and 4, the partition plate 3 is perpendicular to the cross section of the front evaporator 61 in the flow direction of the airflow.

In the present embodiment, it is exemplarily illustrated that the front evaporator 61 is provided in a rectangular parallelepiped shape, and the partition plate 3 is perpendicular to one side of the front evaporator 61 while being kept horizontal, so as to avoid the inclination angle between the flow direction of the airflow and the partition plate 3, and further avoid the airflow flowing along one end of the side wall and forming turbulence, thereby achieving the purpose of reducing the energy loss of the airflow. The arrangement mode can achieve the purpose of accelerating the cooling speed of the interior of the automobile when the vehicle-mounted air conditioner independently refrigerates the front row of the automobile.

As shown in fig. 2 and 3, the front evaporator 61 has a volume greater than that of the rear evaporator 62.

In the present embodiment, it is exemplarily illustrated that the volume ratio of the front evaporator 61 to the rear evaporator 62 is 6:4, so that the front evaporator 61 can be used for circulating more cold sources than the rear evaporator 62, and the refrigerating capacity of the front evaporator 61 is greater than that of the rear evaporator 62; the structure can further accelerate the cooling speed of the interior of the automobile when the vehicle-mounted air conditioner only refrigerates the front row of the automobile.

As shown in fig. 2 and 3, the cross-sectional area of the front evaporator 61 in the flow direction of the airflow is larger than the cross-sectional area of the rear evaporator 62 in the flow direction of the airflow.

In the present embodiment, it is exemplarily illustrated that the rear evaporator 62 is also provided in a rectangular parallelepiped shape, the cross-sectional area of the rear evaporator 62 is equal to the cross-sectional area of the front evaporator 61 in a direction parallel to the partition plate 3, and the height of the front evaporator 61 is greater than the height of the rear evaporator 62, for example, the height ratio of the two is 6: 4. The cross section of the front evaporator 61 and the rear evaporator 62 in the flow direction of the air stream, that is, the heat exchange surface for exchanging heat with the air stream, is increased in size, that is, the size of the heat exchange surface is increased, and thus the above-described structure can further enhance the refrigerating effect of the front evaporator 61.

As shown in fig. 2, 4 and 5, the casing 1 is further provided with a defrosting port 8, and the defrosting port 8 is disposed above the front exhaust port 4 to send the airflow to the front windshield of the automobile. The defroster air port 8 is located in a downstream region of the warm air core 63.

A defroster door 81 is rotatably disposed in the front duct 11, the defroster door 81 includes a first side 811 close to the defroster air port 8 and a second side 812 far from the defroster air port 8, and the defroster door 81 has a closed position, a first open position, and a second open position with respect to the defroster air port 8;

as shown in fig. 2, wherein the defroster air port 8 is blocked by the first side 811 when the defroster air door 81 is in the closed position;

as shown in fig. 5, when the defroster door 81 is rotated to the first open position, the first side 811 is located right above the hot air core 63, and the air flow at least partially heated by the hot air core 63 is sent to the front windshield of the automobile through the defroster air port 8;

as shown in fig. 4, when the defroster door 81 is rotated to the second open position, the first side 811 is located in the upstream region of the warm air core 63, and a part of the air flow in the upstream region of the warm air core 63 is sent directly to the front windshield of the automobile through the defroster air port 8.

In more detail, in the flowing direction of the air flow, the first side 811 is the side downstream of the defroster damper 81, i.e., the side on the left side of the defroster damper 81, and the second side 812 is the side upstream of the defroster damper 81, i.e., the side on the right side of the defroster damper 81.

As shown in fig. 2, it can be understood that when the defrosting damper 81 is in the closed position, one end of the first side 811 away from the rotational position of the defrosting damper 81 abuts against the downstream portion of the defrosting damper 8, that is, the left portion of the defrosting damper 8, at this time, the airflow cannot pass through the defrosting damper 8, the front windshield of the vehicle is not defrosted by the vehicle-mounted air conditioner, and the passenger can control the vehicle-mounted air conditioner to heat or cool the front row of the vehicle by controlling the opening and closing of the mixing damper 72 and the warm air front damper 71, at this time, at least one of the two front dampers 43 is opened.

As shown in fig. 5, when the defrosting damper 81 is rotated to the first open position, if the weather is good and the outdoor temperature is high, the passenger can keep the open state of the front damper 43, open the mixing damper 72, close both the warm air front damper 71 and the warm air rear damper 73, and send cold flow cooled by the front evaporator to the defrosting air outlet 8, so as to defrost the front windshield of the automobile while cooling the front row of the automobile by the vehicle-mounted air conditioner. Of course, the occupant may close both front dampers 43 so that the vehicle air conditioner defrosts only the front windshield of the vehicle.

In an extremely cold weather, the passenger can close the air mixing door 72 and open both the warm front air door 71 and the warm rear air door 73, if at least one of the two front air doors 43 is opened, then the air flow in the front row channel 11 can flow through the warm core 63 to perform heat exchange to form a heat flow, and one part of the heat flow can flow through the front exhaust opening 4 to be sent to the front row of the automobile for heating the front row of the automobile, while the other part of the heat flow can flow through the defrosting opening 8 to be sent to the front windshield of the automobile for defrosting the front windshield, that is, at least part of the air flow heated by the warm core 63 flows through the defrosting opening 8, and the state can be defined as a second heating defrosting mode of the vehicle-mounted air conditioner. Of course, the occupant may close both front dampers 43 to heat only the front row of the automobile.

As shown in fig. 4, when the defrosting damper 81 is rotated to the second open position, if the automobile is in an extremely cold weather, the passenger can open at least one of the two front dampers 43 and close the mixing damper 72, and open both the warm air front damper 71 and the warm air rear damper 73, and at this time, a part of the airflow in the front exhaust passage 11 can flow through the warm air core 63 to exchange heat to form a heat flow, and flow into the downstream area of the warm air core 63; and the other part of the air flow can directly flow through the defrosting port 8 from the upstream area of the hot air core 63 and be sent to the front windshield of the automobile, it can be understood that, because the part of the air flow directly flows through the defrosting port 8, the higher air pressure exists at the defrosting port 8, so that the heat flow flowing into the downstream area of the hot air core 63 is forced to more easily flow through the front exhaust port 4 and not easily flow through the defrosting port 8, therefore, most of the heat flow can be sent to the front row of the automobile through the front exhaust port 4, and only a very small part of the heat flow can flow through the defrosting port 8 together with the part of the air flow which does not flow through the hot air core 63 and be sent to the front windshield of the automobile, which can be defined as a first heating and defrosting mode of the vehicle air conditioner.

Therefore, when the passenger uses the automobile in the extreme cold weather, the passenger can firstly send an instruction to the vehicle-mounted air conditioner so as to start the first heating defrosting mode of the vehicle-mounted air conditioner. In this mode, a part of the airflow in the vehicle air conditioner is heated to a heat flow, and most of the heat flow is sent to the front row of the automobile for heating the front row of the automobile to enhance the comfort of the passengers; meanwhile, the other part of the airflow is directly sent to the front windshield of the automobile without being heated, and is used for defrosting the front windshield for the first time. It can be understood that although the cold flow has a poor defrosting effect, it still has a certain removing effect on the frost mist on the front windshield.

When the front row of the automobile is heated to the designated temperature, the passenger can send an instruction to the vehicle-mounted air conditioner again to start the second heating defrosting mode of the vehicle-mounted air conditioner. Herein, the "specified temperature" may be understood as a temperature at which the occupant feels warm and comfortable in an extremely cold weather. In this mode, the air flow in the on-board air conditioner is all heated to a heat flow, and a part of the heat flow is sent to the front row of the automobile for the passenger to maintain the body temperature; and the other part is sent to the front windshield of the automobile for secondary defrosting of the front windshield of the automobile. It can be understood that the front windshield of the automobile is defrosted through heat flow, frost and fog on the front windshield of the automobile can be effectively removed, and the driving requirement of a passenger when the passenger drives the automobile is met.

The defrosting air door 81 has a closed position, a first open position and a second open position, when the defrosting air door 81 rotates to the first open position, a first heating defrosting mode of the vehicle-mounted air conditioner can be started, in the mode, a part of air flow is heated by the warm air core 63 and then sent to the front row of the automobile for heating the front row of the automobile, and the other part of air flow is directly sent to the front windshield of the automobile for defrosting the front windshield of the automobile for one time; when the defrosting air door 81 rotates to the second opening position, the second heating defrosting mode of the vehicle-mounted air conditioner can be started, in the mode, the air flow is heated by the warm air core 63, at least one part of the heat flow is sent to the front glass of the automobile and is used for secondary defrosting of the front windshield of the automobile, and therefore the purposes of shortening defrosting time, accelerating the temperature rising speed of the front row of the automobile and enhancing the comfort of passengers are achieved.

The application of this application on-vehicle air conditioner's principle does: when passengers are in the front row and the rear row of the automobile, the throttle valve 68 is opened, cold sources can simultaneously enter the front evaporator 61 and the rear evaporator 62 to respectively cool air flows flowing through the front row channel 11 and the rear row channel 12, and the two air flows finally flow to the front row and the rear row of the automobile through the front exhaust port 4 and the rear exhaust port 5 respectively so as to achieve the purpose of refrigerating the front row and the rear row of the automobile; when the automobile only has passengers on the front row and no passengers on the rear row, the throttle valve 68 is closed, the rear evaporator 62 does not work, and the cold source only enters the front evaporator 61, so that the vehicle-mounted air conditioner only refrigerates the front row of the automobile, and the waste of energy is avoided.

Because the partition plate 3 is horizontally arranged and the partition plate 3 is vertical to the front evaporator 61, when the partition plate 3 guides the airflow in the front row channel 11, the part of the airflow can pass through the front evaporator 61, so that the air resistance can be reduced in the heat exchange process, the heat exchange efficiency can be enhanced, and the purpose of obtaining better refrigeration effect by using limited energy sources is achieved; due to the principle that one end of the partition plate 3 extends to the position above the maximum height of the front exhaust opening 4 by the front evaporator 61, the partial air flow can reduce the turning times and flow from the front exhaust opening 4 to the front row of the automobile in a shorter path, so that the purpose of reducing the energy loss of the air flow in the circulating process is achieved. To sum up, this application improves the cryogenic effect of on-vehicle air conditioner through reducing air-resistor, reinforcing heat exchange efficiency and reduction energy loss matched with mode when only refrigerating the front bank of car to the inside rapid cooling to the car, and then reinforcing passenger's experience is felt.

The application also provides an automobile which comprises any one of the vehicle-mounted air conditioners provided by the application.

The technical features of the above embodiments can be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the above embodiments are not described, but should be considered as the scope of the present specification as long as there is no contradiction between the combinations of the technical features.

The above-mentioned embodiments only express several embodiments of the present application, and the description thereof is specific and detailed, but not to be understood as limiting the scope of the invention. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the concept of the present application, which falls within the scope of protection of the present application. Therefore, the protection scope of the present patent application shall be subject to the appended claims.

Claims

1. An in-vehicle air conditioner, characterized in that, the in-vehicle air conditioner includes:

a shell (1) which is arranged in a hollow way, and the top of the shell is provided with an air inlet mechanism (2) used for sending airflow into the shell (1);

the separation plate (3) is horizontally arranged in the shell (1) and divides the inner space of the shell (1) into an upper front-row channel (11) and a lower rear-row channel (12), a front-row air outlet (4) is formed in the position of the front-row channel (11) of the shell (1) and used for enabling the air flow to enter the front row of the automobile, and a rear-row air outlet (5) is formed in the position of the rear-row channel (12) of the shell (1) and used for enabling the air flow to enter the rear row of the automobile;

and the adjusting mechanism (6) comprises a front evaporator (61) and a rear evaporator (62) which are respectively arranged in a front row channel (11) and a rear row channel (12), the rear evaporator (62) is configured with an active state and a non-active state, the front evaporator (61) is vertical to the partition plate (3), one end of the front evaporator (61) extends to the partition plate (3), and the other end of the front evaporator extends to the position of the maximum height of the front exhaust opening (4).

2. The vehicle air conditioner according to claim 1,

the adjusting mechanism (6) further comprises a warm air core (63) partially arranged in the front row passage (11) and partially arranged in the rear row passage (12) for heating the air flow, the warm air core (63) being arranged in parallel with the front evaporator (61).

3. The vehicle air conditioner of claim 2,

be provided with floor (13) in casing (1), floor (13) level set up in front row passageway (11), one side of floor (13) with warm braw core (63) are located one end butt in front row passageway (11), and will front row passageway (11) are separated and are close to warm braw passageway (111) of division board (3) and keep away from cold wind passageway (112) of division board (3), still rotate in casing (1) and be provided with preceding air door of warm braw (71) and air door mixing (72), preceding air door of warm braw (71) with air door mixing (72) rotate to the level in order respectively with warm braw passageway (111) with cold wind passageway (112) are opened to rotate to vertical in order respectively with warm braw passageway (111) with cold wind passageway (112) are closed.

4. The vehicle air conditioner of claim 3,

the front exhaust air port (4) comprises a front blowing surface air port (41) and a front blowing foot air port (42), the front blowing surface air port is located at the upper position, the front blowing foot air port is located at the lower position, the height position, used for the rotating shaft of the air mixing door (72), of the air mixing door is smaller than the maximum height position of the front blowing surface air port (41), and the height position, used for the rotating shaft of the warm air front air door (71), of the warm air front air door is smaller than the maximum height position of the front blowing foot air port (42).

5. The vehicle air conditioner of claim 3,

still rotate in casing (1) and be provided with air door (73) behind the warm braw, air door (73) set up behind the warm braw rib plate (13) are kept away from the one end of air door (71) before the warm braw, air door (73) rotate behind the warm braw to vertical with warm braw core (63) is located part in front-seat passageway (11) is sealed, rotates to the level in order to keep the open mode of warm braw passageway (111).

6. The vehicle air conditioner of claim 5,

both ends of floor (13) all are provided with deflector (14), deflector (14) are along being close to the direction flaring of division board (3) extends, before the warm braw air door (71) with air door (73) rotate respectively with one behind the warm braw when vertical division board (3) looks butt.

7. The vehicle air conditioner according to claim 1,

the partition plate (3) is perpendicular to the cross section of the front evaporator (61) in the flow direction of the air stream.

8. The vehicle air conditioner of claim 1,

the volume of the front evaporator (61) is greater than the volume of the rear evaporator (62).

9. The vehicle air conditioner according to claim 1,

the cross-sectional area of the front evaporator (61) in the flow direction of the airflow is larger than the cross-sectional area of the rear evaporator (62) in the flow direction of the airflow.

10. An automobile, characterized in that the automobile comprises the vehicle air conditioner as recited in any one of claims 1 to 9.