JPH0395368A - Condenser - Google Patents

Abstract

PURPOSE:To enable the condition of a refrigerant at an outlet of a condenser to be controlled without providing a receiver in a refrigeration cycle, by enlarging the flow passage area at an intermediate position of a refrigerant passage, and controlling the condition of gas-liquid separation by a gas-liquid separating part deprived of fins. CONSTITUTION:A gaseous refrigerant releases heat in heat exchange with the outside air through fins 6a, is then brought into a condensate-gas two-phase state at a main condenser part, and is introduced into a receiver tube 7 of a gas-liquid separating part 2. The refrigerant in the tube 7 does not release heat, although it is in the two- phase state and has a flow velocity ratio between the gaseous phase and the liquid phase thereof. Therefore, the refrigerant is fed out to an auxiliary condenser part 3 with no variations in the proportions of the gaseous and liquid phases. The refrigerant is condensed by cooling in the condenser part 3, and the resultant liquid refrigerant is discharged through a refrigerant outlet at a lower end. The condition of the refrigerant at this moment, namely, the presence or absence of bubbles is verified through a sight glass 11, whereby the amount of charge of the refrigerant is inspected. Before defoaming, the auxiliary condenser part 3 functions to condense the refrigerant, similarly to the main condenser part 1. After deforming, the auxiliary condenser part 3 functions for both condensation and supercooling.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a condenser used for car air conditioners and the like.

[Prior Art] In recent years, condensers for car air conditioners, etc., have been constructed by alternately stacking refrigerant tubes and heat dissipation fins, and providing partition plates inside, as shown in Japanese Patent Laid-Open Publication No. 63-34466, for example. A so-called serpentine type header has been proposed in which a header is connected to both ends of the refrigerant tube, but compared to a so-called serpentine type header in which the refrigerant tube is bent in a serpentine shape, It is easy to manufacture, has a good heat exchange rate, and is not subject to dimensional restrictions due to bending of the refrigerant tube like the surventine type, so it can be made smaller and is attracting attention, especially for use in car air conditioners.

In addition, in conventional refrigeration cycles such as car air conditioners where the conditions on the refrigerant outlet side of the condenser tend to fluctuate, a receiver for gas-liquid separation is installed in the condenser outlet piping to temporarily store refrigerant. This controls the refrigerant condition at the condenser outlet.

This means that the number of parts that make up the refrigeration cycle will increase, resulting in lower parts costs, assembly costs for vehicles, etc.
As a result, costs will increase.

[Problem to be solved by the invention]

The present invention has been made in view of the above-mentioned circumstances, and by providing a condenser with a new configuration and providing a gas-liquid separation function in addition to the conventional condensation function, there is no need to provide a receiver in the refrigeration cycle. The present invention also aims to provide a condenser that can control the refrigerant state at the outlet of the condenser and is particularly suitable for use in car air conditioners.

[Means to solve the problem]

In order to achieve the above object, the present invention includes a refrigerant passage pipe that constitutes a meandering refrigerant passage as a whole, and fins joined to the refrigerant passage pipe, and the present invention includes a refrigerant passage pipe that forms a meandering refrigerant passage as a whole, and fins that are joined to the refrigerant passage pipe, so that the refrigerant flow flowing through the refrigerant passage pipe is controlled. A condenser that condenses by dissipating heat through the fins, in which the flow area of the refrigerant passage pipe is widened and a gas-liquid separation section is provided in which the fins are removed, in the middle of the refrigerant passage. The refrigerant flow is characterized by controlling the gas-liquid separation state of the refrigerant flow by a liquid separation section.

(Function, Effect) Therefore, with the gas-liquid separation section, the condenser has the function of gas-liquid separation, which was previously handled by the I/seiver, and the 'a condenser Refrigerant conditions at the outlet can be controlled.

〔Example〕

Hereinafter, the present invention will be explained based on embodiments shown in the drawings.

A schematic structural diagram of the first embodiment of the present invention is shown in Fig. 1. In FIG. 1, 1 is a main condenser section, 2 is a gas-liquid separation section, and 3 is an auxiliary condenser section.

The main capacitor section 1 is structured in the above-mentioned header type,
Refrigerant tube 5a... and heat radiation fin 6a...
It consists of a core part 4 in which... are laminated alternately, and header parts 8A and 9A connected to both left and right sides of this core part 4.
The refrigerant tubes 5a are formed of, for example, single flat tubes or porous flat tubes whose interior is divided into a plurality of passages, while the heat dissipation fins 6
a... is made of plate fins or corrugated fins. In addition, the fin 6a is...
The refrigerant tube 5a is joined to the side surface of the refrigerant tube 5a by brazing or soldering. The inside of the header 8A is divided into upper and lower sections by a partition wall 10A provided at a position slightly below the center; The outlet side chamber 1b is configured to send out the lower refrigerant to be sent out.

The gas-liquid separation section 2 includes refrigerant tubes 5a and 5a of the main condenser section 1.
The refrigerant from the main condenser section 1 is sent to the auxiliary condenser section 3 through a receiver tube 7, which is a meandering single tube with a larger diameter than the receiver tube 7. Note that if the inner diameter is made too large, only gas refrigerant will flow, so it is set so that liquid refrigerant also flows.

The auxiliary capacitor section 3 is structured in a header type like the main capacitor section 1 described above, and includes refrigerant tubes 5C...
It consists of a core part 4 in which heat dissipation fins 6C, . In addition,
As will be described later, since the auxiliary condenser section 3 is a liquid refrigerant obtained by condensing the refrigerant flow from the gas-liquid separation section 2, it does not need to have a multilayer structure like the main condenser section 1, and has a header as shown in the figure. A simple meandering shape may be provided by the partition wall 10C provided therein.

Alternatively, it may be a simple surventine type.

Further, in the figure, 11 is a sight glass for checking the amount of refrigerant charged.

Next, how the refrigerant is reduced by 4'' in the above structure will be explained in order.

The inside of the header 8A of the main capacitor part 1 is divided into upper and lower parts by the partition wall 10 as described above, and the artificial side chamber 1a
A gas refrigerant is supplied to the refrigerant from a refrigerant inlet provided at the upper end.

The supplied gaseous refrigerant flows through the tube 5a connecting the inlet side chamber 1a and the header 9A, and is cooled during this time and passes through the header 9A.
Leading to A. The gas refrigerant flows downward within the header 9A, passes through another tube 5a, and reaches the outlet side chamber 1b of the header 8A.

That is, the gaseous refrigerant fed under pressure from the compressor passes through the fins 6a while passing through the tube 5a of the main condenser section l.
It exchanges heat with the outside air via... and radiates heat, and is condensed into a two-phase state of condensed liquid and gas.

Then, the proportion occupied by the condensed liquid increases and is sent to the gas-liquid separation section 2.

The refrigerant flow in a two-phase state of condensed liquid and gas in the main condenser section is introduced into the next refrigerant passage of the gas-liquid separation section 2, that is, the receiver tube 7. Although the refrigerant in this receiver tube 7 has a gas-liquid two-phase flow velocity ratio, #k compression does not occur because heat is not released, that is, the refrigerant flow does not change without changing the gas-liquid ratio. It is sent to the auxiliary capacitor section 3.

In the auxiliary condenser section 3, the refrigerant flow is cooled and condensed into liquid refrigerant in the same manner as in the main condenser section 1 described above, and the liquid refrigerant is sent out from the refrigerant outlet at the lower end. The refrigerant charging amount is checked by checking the state of the refrigerant at that time, that is, the presence or absence of bubbles through the sight glass l1.

Next, the operation of this embodiment will be explained by giving a specific example.

For example, in Fig. 1, if the sizes of the main condenser section 1 and the auxiliary condenser section 3 are configured to 9 = 1, the disappearance of bubbles in the sight glass 1l during refrigerant filling will be caused by the dryness of the refrigerant at the outlet of the main condenser section. 0. It corresponds to being 1.

As mentioned above, since heat is not radiated in the gas-liquid separation section 2, no condensation occurs in the receiver tube 7, and the dryness level is O everywhere inside the receiver tube 7. It is 1. That is, the ratio of the condensing capacities of the main condenser section 1 and the auxiliary condenser section 3 determines the degree of dryness in the gas-liquid separation section 2 located in the middle thereof. Note that the degree of dryness in the gas-liquid separation section 2 is 0. 1, for example, when R12 is used as the refrigerant, the pressure is 1
5kg/cn! In G, the gas:liquid volume ratio is about 10:7.

Next, when refrigerant is further charged with the above configuration, the dryness of the refrigerant at the outlet of main condenser section 1, that is, the dryness of the refrigerant at the outlet of main condenser section 1
The degree of dryness in the receiver tube 7 decreases, and the amount of liquid refrigerant in the receiver tube 7 increases rapidly. When the degree of dryness in the gas-liquid separation section 2 was 0.1, the refrigerant at the condenser refrigerant outlet was a saturated liquid refrigerant due to Wi condensation in the auxiliary condenser section 3, but as the refrigerant filling amount increased, the refrigerant became a saturated liquid refrigerant. Due to the decrease in dryness in the separator 2, the refrigerant from the condenser refrigerant outlet is sent out with a certain degree of supercooling due to the heat exchange effect in the auxiliary condenser section 3.At the condenser outlet, the refrigerant is supercooled. To be careful,
As shown in the P-i characteristic diagram in Figure 2, the enthalpy difference of the refrigerant in the condenser is large, indicating that the heat exchange capacity is improved, and in turn, the enthalpy difference in the evaporator in the refrigeration cycle is large. Refrigeration capacity can be improved because it can be removed. For example, by increasing the amount of refrigerant charged, the dryness of the refrigerant at the outlet of main condenser section 1 can be reduced to 0. 1 to 0.05
Assuming that, the receiver tube 7 of the gas-liquid separation section 2
When the refrigerant is R12, the air:liquid volume ratio is approximately 2=3.
becomes. That is, if the receiver channel volume is, for example, 3
If it is 0 0 cc, then the dryness is 0. 1 to 0
．． 05, the volume of liquid cooling medium occupying the inside of the receiver tube 7 increases from 123cc to 180cc. As the amount of liquid refrigerant flowing into the auxiliary condenser section 3 increases, the refrigerant at the outlet of the auxiliary condenser section 3, that is, at the condenser refrigerant outlet, has a degree of subcooling. Note that the pressure increase on the high pressure side of the refrigeration cycle due to the increase in liquid volume in the receiver tube is 0. 1
kg/CIi1 or less, and there is no problem.

As described above, the role of the auxiliary condenser section 3 differs depending on the state of the refrigerant in the sight glass 11. That is, before the bubbles disappear, like the main condenser section 1, it acts on refrigerant condensation, while after the bubbles disappear, it has two functions: condensation and supercooling.

The refrigerating capacity of the refrigerating cycle at that time increases due to the influence of the degree of supercooling after the bubbles disappear, as shown in FIG. In addition, in FIG. 3, curve X is the refrigeration capacity characteristic of the refrigeration cycle using the condenser of this embodiment, and curve Y is the refrigeration capacity characteristic of the conventional refrigeration cycle.

In addition, by further increasing the amount of refrigerant charged, the main condenser section 1
If the refrigerant dryness at the outlet is 0, the receiver tube 7 of the gas-liquid separation section 2 will be filled with saturated liquid refrigerant. In addition, an increase in the filling amount beyond that will result in refrigerant overfilling.

In the first embodiment, the gas-liquid separation section 2 is formed by bending a single tube into a meandering shape, but as shown in FIG. The refrigerant passage may be of a header type and have a meandering refrigerant passage provided by a partition wall (second embodiment). In Figure 4, 8B,
Reference numeral 9B indicates left and right headers of the gas-liquid separation section 2, IOB indicates a partition wall, and the other configurations are the same as those shown in FIG. 1 and are given the same reference numerals. This product is easier to manufacture because the main capacitor section 1, gas-liquid separation section 2, and auxiliary capacitor section 3 are all laminated, that is, integrated into a header type structure. It is particularly suitable for use in car air conditioners.

In addition, in the first and second embodiments described above, the headers were of a horizontal type with headers placed on the left and right sides of the device, but as shown in the third embodiment of FIG. It may be. In addition, in Figure 5, Figures 1 and 4
Components that are the same as those in the figure are given the same reference numerals. This thing is
In the gas-liquid separation section 2, it is not necessary to provide a partition wall 10B to form a meandering refrigerant passage as shown in FIG. 4, and instead, as shown in FIG. The shape may be formed by arranging tubes in parallel. Furthermore, the outlet of the gas-liquid separation section 2 for introducing into the auxiliary condenser section 3 is provided in the lower header section 9, and the refrigerant introduced into the auxiliary condenser section 3 can be only saturated liquid refrigerant. , the auxiliary capacitor section 3 functions to subcool the refrigerant. Note that the sight glass 11 is installed in the upper header section 8 immediately after the gas-liquid separation section 2, and the state of the refrigerant introduced into the auxiliary condenser section 3 is monitored to check the amount of refrigerant charged.

In the various embodiments described above, the header 8A of the main condenser section 1 is divided into the inlet side chamber 1a and the outlet side chamber 1 by the partition wall 10A.
Although the header 9A can also be divided by a partition wall and the refrigerant flow can meander multiple times through the header 9A. .

In addition, in the various embodiments described above, the main capacitor section 1
Alternatively, the auxiliary capacitor section 3 was arranged in a header type, but the conventional serventine type,
Alternatively, a multi-bath type surventine type with parallel refrigerant passages to reduce refrigerant pressure loss may also be used.

[Brief explanation of drawings]

Fig. 1 is a schematic structural diagram of the first embodiment of the present invention, Fig. 2 is a P-i characteristic diagram of a refrigeration cycle, Fig. 3 is a characteristic diagram showing the relationship between cooling capacity and refrigerant charging amount, and Fig. The figure is a schematic structural diagram of the second embodiment of the present invention, and Fig. 5 is a schematic structural diagram of the third embodiment of the present invention.1... Main condenser section, la... Inlet side chamber, lb.
...Exit side room. 2... Gas-liquid separation section, 3... Capacitor section 4... Core section, 5a, 5c... Refrigerant tube, 6a, 6c... Radiation fin. 7...Receiver tube. 888~8C, 9.9A~9C...Header part,
10A~1. OC...Partition wall, 11...Sight glass.

Claims (2)

[Claims] (1) By providing a refrigerant passage pipe that constitutes a meandering refrigerant passage as a whole and fins joined to the refrigerant passage pipe, heat is radiated from the refrigerant flow flowing through the refrigerant passage pipe through the fins. A condenser for condensing, in which a gas-liquid separation part is provided in the middle of the refrigerant passage, in which the flow area of the refrigerant passage pipe is widened and the fins are removed, and the gas-liquid separation part separates the air from the refrigerant flow. A condenser characterized by controlling the state of liquid separation and allowing the liquid to flow. (2) In order to further condense or supercool the refrigerant flow from the gas-liquid separation section, the auxiliary condenser consists of a refrigerant passage pipe that constitutes a meandering refrigerant passage as a whole, and fins joined to this refrigerant passage pipe. The condenser according to claim 1, further comprising a auxiliary condenser section and a downstream side of the gas-liquid separation section.