Patent Description:
A housing of a condenser contains heat exchange tubes; an inlet pipe of the condenser is generally arranged at an upper part of the condenser, and gaseous fluid enters the housing of the condenser through the inlet pipe of the condenser. Since the speed of the gaseous fluid is relatively high, the gaseous fluid can easily cause the heat exchange tubes to rupture if it strikes them directly.

For example, <CIT>, which can be considered as the closest prior art, relates to a shell-side condenser inlet diffuser for a vapor compression refrigeration system. The diffuser includes an inlet to receive a compressed refrigerant from a compressor of the refrigeration system. A chamber is in fluid communication with the inlet to receive compressed refrigerant, the chamber having an upper side and a lower side and lateral sides bridging the upper and lower sides, the chamber having a plurality of openings to discharge refrigerant inside the condenser. A protrusion is disposed inside the chamber. The protrusion and the chamber are configured and disposed to diffuse and direct a flow of refrigerant from the compressor to inside the condenser, the refrigerant leaving the chamber having a higher pressure level than the refrigerant entering the chamber.

A demonstrative embodiment of the present application can solve at least some of the abovementioned problems.

The invention is solely defined by the appended claims.

The condenser of the present application can reduce frictional loss and local resistance of a refrigerant gas flowing into the inlet pipe, such that dynamic pressure of the refrigerant gas entering the condenser is partially converted to static pressure, and a static pressure loss when the refrigerant gas enters the tubular body through the inlet is reduced, thereby increasing the condensing pressure of the refrigerant gas in the condenser, so as to enhance the heat exchange performance.

A better understanding of the features and advantages of the present application can be gained by reading the following detailed explanation with reference to the drawings; in all of the drawings, identical reference labels indicate identical components, wherein:.

Various particular embodiments and aspects are described below with reference to the accompanying drawings, which form part of this Description. It should be understood that although terms indicating direction, such as "front", "rear", "up", "down", "left" and "right", etc. are used in the present invention to describe various demonstrative structural parts and elements of the present invention in a directional or orientational manner, these terms are used here purely in order to facilitate explanation, and are determined on the basis of demonstrative orientations shown in the drawings. Since the embodiments and aspects disclosed in the present invention may be arranged in accordance with different directions, these terms indicating direction are purely illustrative, and should not be regarded as limiting. In the drawings below, identical components use identical reference labels, and similar components use similar reference labels.

<FIG> is a three-dimensional drawing of a condenser <NUM> in an aspect of the present application. <FIG> is a sectional view, taken along section line A-A in <FIG>, of the condenser <NUM> in <FIG>. <FIG> is a sectional view, taken along section line B-B in <FIG>, of the condenser <NUM> in <FIG>. As shown in <FIG>, the condenser <NUM> comprises a housing <NUM>. The housing <NUM> comprises a tubular body <NUM>, a left dividing plate <NUM>, a right dividing plate <NUM>, a left end plate <NUM> and a right end plate <NUM>. The tubular body <NUM> is formed to extend in a length direction of the condenser <NUM>. Left and right ends of the tubular body <NUM> are closed by the left dividing plate <NUM> and right dividing plate <NUM> respectively, so as to form an accommodating cavity <NUM>. The left end plate <NUM> is arc-shaped; the left end plate <NUM> is connected to the left dividing plate <NUM> to form a communicating cavity <NUM>. The right end plate <NUM> is also arc-shaped; the right end plate <NUM> is connected to the right dividing plate <NUM>. The right dividing plate <NUM> further comprises a transverse dividing plate <NUM> extending transversely from the right dividing plate <NUM> to the right end plate <NUM>, thereby forming an outlet accommodating cavity <NUM> and an inlet accommodating cavity <NUM>. The housing <NUM> further comprises a medium inlet pipe <NUM> and a medium outlet pipe <NUM>; the medium inlet pipe <NUM> and medium outlet pipe <NUM> are disposed on the right end plate <NUM>, the medium inlet pipe <NUM> being in fluid communication with the inlet accommodating cavity <NUM>, and the medium outlet pipe <NUM> being in fluid communication with the outlet accommodating cavity <NUM>.

As shown in <FIG> and <FIG>, the condenser <NUM> further comprises a first tube bundle <NUM>, and a second tube bundle <NUM> located below the first tube bundle <NUM>. The first tube bundle <NUM> and second tube bundle <NUM> are horizontally installed in the accommodating cavity <NUM>, and extend in the length direction of the condenser <NUM>. One end of the first tube bundle <NUM> is in fluid communication with the communicating cavity <NUM>, and another end of the first tube bundle <NUM> is in fluid communication with the outlet accommodating cavity <NUM>; one end of the second tube bundle <NUM> is in fluid communication with the communicating cavity <NUM>, and another end of the second tube bundle <NUM> is in fluid communication with the inlet accommodating cavity <NUM>, such that a cooling medium can pass through the medium inlet pipe <NUM> and then flow through the inlet accommodating cavity <NUM>, the second tube bundle <NUM>, the communicating cavity <NUM>, the first tube bundle <NUM> and the outlet accommodating cavity <NUM> in sequence, and flow out of the condenser <NUM> via the medium outlet pipe <NUM> (in the flow direction indicated by the arrows M in <FIG>). The condenser <NUM> further comprises an inlet pipe <NUM> and an outlet pipe <NUM>. The inlet pipe <NUM> is located at an upper part of the tubular body <NUM>, and configured to receive a refrigerant gas. The outlet pipe <NUM> is located at a lower part of the tubular body <NUM>, and configured to discharge condensed refrigerant liquid from the tubular body <NUM>. The refrigerant gas that flows into the tubular body <NUM> through the inlet pipe <NUM> undergoes heat exchange with a medium in the first tube bundle <NUM> and second tube bundle <NUM>, and after being condensed into refrigerant liquid, can be discharged from the tubular body <NUM> via the outlet pipe <NUM>.

The condenser <NUM> further comprises an anti-impact plate <NUM>. As an example, the anti-impact plate <NUM> is substantially a flat plate and is installed transversely in the accommodating cavity <NUM>. The anti-impact plate <NUM> is arranged below the inlet pipe <NUM>, and located above the first tube bundle <NUM>, such that when the refrigerant gas flows into the tubular body <NUM> through the inlet pipe <NUM> at a relatively high speed, the anti-impact plate <NUM> can prevent the refrigerant gas from directly striking the first tube bundle <NUM>, so as to avoid rupture of the first tube bundle <NUM>. In addition, the anti-impact plate <NUM> is also arranged to be separated from an outlet <NUM> of the inlet pipe <NUM> by a gap H, so that refrigerant fluid can flow toward the first tube bundle <NUM> and second tube bundle <NUM> after flowing out of the outlet <NUM>. The anti-impact plate <NUM> is welded to the tubular body <NUM> by means of a pair of connecting rods <NUM>.

<FIG> is an enlarged drawing of the part enclosed by dotted lines in <FIG>, intended to show in greater detail an aspect of the structure of the inlet pipe <NUM> and the anti-impact plate <NUM>. As shown in <FIG>, the inlet pipe <NUM> is a round pipe with an internal diameter that gradually increases from an inlet <NUM> to the outlet <NUM>, and has a central axis K. The inlet pipe <NUM> passes through an upper part of the housing <NUM>, and the outlet <NUM> of the inlet pipe <NUM> is accommodated in the accommodating cavity <NUM>. The inlet <NUM> of the inlet pipe <NUM> has internal diameter D<NUM>, and the outlet <NUM> of the inlet pipe <NUM> has internal diameter D<NUM>; the internal diameter of the inlet pipe <NUM> increases smoothly from the internal diameter D<NUM> of the inlet <NUM> to the internal diameter D<NUM> of the outlet <NUM>. On the anti-impact plate <NUM>, the outlet <NUM> of the inlet pipe <NUM> has a projected region S projected vertically downward along the central axis K of the inlet pipe <NUM>. The projected region S is a hole-free zone, so that the refrigerant gas can flow past at least a part of an edge of the anti-impact plate <NUM> along an upper surface of the anti-impact plate <NUM> and then come into contact with the first tube bundle <NUM>, thereby preventing the refrigerant gas from striking the first tube bundle <NUM> directly.

<FIG> is a schematic drawing of part of an axial section of the inlet pipe <NUM> in <FIG>, intended to show the specific shape of an inner wall of the inlet pipe <NUM>. Here, x represents distance of the inner wall of the inlet pipe <NUM> on the axial section, in a direction perpendicular to the central axis K; y represents distance of the inner wall of the inlet pipe <NUM> on the axial section, in a direction parallel to the central axis K. In the axial section, a curve of the inner wall of the inlet pipe <NUM> satisfies any one or more of the following curves, wherein f, g, h, l, m, n, o, p, q, s, u and v represent constants:.

The smooth and gradual widening of the internal diameter of the inlet pipe <NUM> from the internal diameter D<NUM> of the inlet <NUM> to the internal diameter D<NUM> of the outlet <NUM> can reduce frictional loss of the refrigerant gas flowing into the inlet pipe <NUM>, and this kind of gradually widening structure can also reduce local resistance of the refrigerant gas.

As an example, the inlet pipe <NUM> is a pipe of equal thickness. As another example, the inlet pipe may also be a pipe of non-equal thickness.

<FIG> is a schematic chart of the variation of a pressure recovery coefficient Cv of the inlet pipe <NUM> in <FIG> with respect to a ratio AreaRatio. Here, the inlet <NUM> of the inlet pipe <NUM> has an inlet area A<NUM>, a surface formed by vertically downward extension of an edge of the outlet <NUM> of the inlet pipe <NUM> to the anti-impact plate (<NUM>) has an outlet extension area A<NUM>, and the ratio AreaRatio represents the ratio of the inlet area A<NUM> to the outlet extension area A<NUM>. The pressure recovery coefficient Cv represents the ratio of conversion of dynamic pressure of the refrigerant gas entering the condenser <NUM> to static pressure. For example, when the pressure recovery coefficient Cv is <NUM>, this indicates that <NUM>% of dynamic pressure is converted to static pressure. Specifically, when the ratio AreaRatio satisfies the following formula, the structural arrangement of the inlet pipe <NUM> and anti-impact plate <NUM> can cause the dynamic pressure of the refrigerant gas entering the condenser <NUM> to be partially converted to static pressure and reduce the static pressure loss when the refrigerant gas enters the tubular body <NUM> through the inlet <NUM>, thereby increasing the condensing pressure of the refrigerant gas in the condenser <NUM>, so as to enhance the heat exchange performance.

As shown in <FIG>, the relationship between the pressure recovery coefficient Cv and the ratio AreaRatio satisfies: <MAT>.

As an example, the range of values of the ratio AreaRatio = A<NUM>/A<NUM> is greater than or equal to <NUM> and less than or equal to <NUM>.

<FIG> are schematic drawings of the relative positional relationship of the inlet pipe <NUM> and the anti-impact plate <NUM> in the condenser shown in <FIG>, wherein <FIG> is intended to show the inlet area A<NUM> of the inlet <NUM>, and <FIG> are intended to show the outlet extension area A<NUM>. As shown in <FIG>, the shaded part in <FIG> indicates the inlet area A<NUM> of the inlet <NUM>, wherein the inlet area A<NUM> is determined by the internal diameter D<NUM> of the inlet <NUM>. Specifically, the inlet area A<NUM> and the internal diameter D<NUM> of the inlet <NUM> satisfy: <MAT>.

The surface formed by vertically downward extension of the edge of the outlet <NUM> to the anti-impact plate <NUM> is an imaginary surface, which is a cylindrical surface and has the outlet extension area A<NUM>.

As shown in <FIG>, the sum of a shaded part A<NUM> in <FIG> and a shaded part A<NUM> in <FIG> is the outlet extension area A<NUM>. Specifically, the shaded part A<NUM> in <FIG> represents a part of the outlet extension area A<NUM> that is visible at the visual angle of <FIG> (which is the same as the visual angle of <FIG>), and the shaded part A<NUM> in <FIG> represents another part of the outlet extension area A<NUM> that is not visible at the visual angle of <FIG> (which is the same as the visual angle of <FIG>).

More specifically, the area A<NUM>, the internal diameter D<NUM> of the outlet <NUM>, and the gap H between the outlet <NUM> and the anti-impact plate <NUM> satisfy: <MAT>.

That is, the outlet extension area A<NUM> is related to the circumference of the outlet <NUM> and the gap H between the outlet <NUM> and the anti-impact plate <NUM>.

<FIG> is a sectional view, taken along section line A-A in <FIG>, of the condenser <NUM> according to another aspect of the present application. <FIG> is a sectional view, taken along section line B-B in <FIG>, of the condenser <NUM> in <FIG>. In the condenser <NUM> shown in <FIG>, except for the different structure of the anti-impact plate <NUM>, the configurations of all the other components are the same as in <FIG>, so are not described again here. Specifically, in the aspect shown in <FIG>, two side edges of the anti-impact plate <NUM> in a width direction of the condenser <NUM> (i.e. perpendicular to the length direction of the tubular body <NUM>) are bent upward, to form extension parts <NUM>, <NUM> extending upward, and a connection with the housing <NUM> is made by means of the two side edges of the anti-impact plate <NUM> in the width direction of the condenser <NUM>.

<FIG> are schematic drawings of the relative positional relationship of the inlet pipe <NUM> and the anti-impact plate <NUM> in the aspect shown in <FIG>, wherein <FIG> is intended to show the inlet area A<NUM> of the inlet <NUM>, and <FIG> are intended to show the outlet extension area A<NUM> of the surface formed by vertically downward extension of the edge of the outlet <NUM> to the anti-impact plate <NUM>. The area A<NUM> of the inlet <NUM> shown in <FIG> and the method of calculation thereof are the same as in <FIG>, so are not described again here. As shown in <FIG>, the sum of a shaded part A<NUM> in <FIG> and shaded parts A<NUM>, A<NUM> in <FIG> is the outlet extension area A<NUM>. Specifically, the shaded part A<NUM> in <FIG> represents a part of the outlet extension area A<NUM> that is visible at the visual angle of <FIG> (which is the same as the visual angle of <FIG>), the shaded part A<NUM> in <FIG> represents a part of the outlet extension area A<NUM> that is obscured by the inlet pipe <NUM> at the visual angle of <FIG> (which is the same as the visual angle of <FIG>), and the shaded part A<NUM> in <FIG> represents a part of the outlet extension area A<NUM> that is obscured by the extension part <NUM> of the anti-impact plate <NUM> at the visual angle of <FIG> (which is the same as the visual angle of <FIG>).

It must be explained that in the aspect shown in <FIG>, the surface of vertically downward extension of the edge of the outlet <NUM> to the anti-impact plate <NUM> is a cylindrical surface (i.e. annular). However, in the aspect shown in <FIG>, the surface formed by vertically downward extension of the edge of the outlet <NUM> to the anti-impact plate <NUM> is not a cylindrical surface. Specifically, the surface formed by vertically downward extension of the edge of the outlet <NUM> strikes the extension parts <NUM>, <NUM> of the anti-impact plate <NUM>, so a cylindrical surface formed by vertically downward extension of the edge of the outlet <NUM> will have a part cut away by the extension parts <NUM>, <NUM>; thus, the surface formed by vertically downward extension of the edge of the outlet <NUM> is not cylindrical between the outlet <NUM> and the anti-impact plate <NUM>. Therefore, the outlet extension area A<NUM> is not only related to the circumference of the outlet <NUM> and the gap H between the outlet <NUM> and the anti-impact plate <NUM>, but also related to the structural shape of the anti-impact plate <NUM>.

<FIG> is a sectional view, taken along section line A-A in <FIG>, of the condenser <NUM> according to the invention. In the condenser <NUM> shown in <FIG>, except for the different structure of the anti-impact plate <NUM>, the configurations of all the other components are the same as in <FIG>, so are not described again here. Specifically, according to the invention as shown in <FIG>, the anti-impact plate <NUM> is provided with multiple holes <NUM>; all of the multiple holes <NUM> are located outside the projected region S, on the anti-impact plate <NUM>, of the outlet <NUM> of the inlet pipe <NUM>, projected vertically downward along the central axis K of the inlet pipe <NUM>, so that the refrigerant gas can flow toward the first tube bundle <NUM> more quickly via the multiple holes <NUM> after being blocked by the anti-impact plate <NUM>. Although the anti-impact plate <NUM> is provided with the multiple holes <NUM>, since the anti-impact plate <NUM> under the projected region S is still a flat plate, in the embodiment shown in <FIG>, the inlet area A<NUM> of the inlet <NUM> and the outlet extension area A<NUM> of vertically downward extension of the edge of the outlet <NUM> to the anti-impact plate <NUM> are calculated in the same way as that expounded in <FIG>.

It must be explained that although the anti-impact plate in the present application is substantially configured as a flat plate in each case, those skilled in the art will understand that the anti-impact plate could also be designed to have another shape structure more favorable for the flow of refrigerant gas.

Claim 1:
A condenser (<NUM>) comprising:
- a housing (<NUM>), having an accommodating cavity (<NUM>);
- an inlet pipe (<NUM>), the inlet pipe (<NUM>) being a round pipe with an internal diameter that gradually increases from an inlet (<NUM>) to an outlet (<NUM>), wherein the inlet pipe (<NUM>) is configured to pass through an upper part of the housing (<NUM>), and the outlet (<NUM>) of the inlet pipe (<NUM>) is accommodated in the accommodating cavity (<NUM>); and
- an anti-impact plate (<NUM>), accommodated in the accommodating cavity (<NUM>) and located below the outlet (<NUM>) of the inlet pipe (<NUM>), and a gap (H) being provided between the anti-impact plate (<NUM>) and the outlet (<NUM>), the gap allowing through-flow of a fluid flowing out of the outlet (<NUM>),
characterized in that:
the anti-impact plate (<NUM>) is provided with multiple holes (<NUM>), all of which are located outside a projected region (S) on the anti-impact plate (<NUM>), the projected region (S) corresponding to the outlet (<NUM>) of the inlet pipe (<NUM>) projected vertically downward along a central axis (K) of the inlet pipe (<NUM>), and the projected region (S) being a hole-free zone.