BRIEF DESCRIPTION OF THE DRAWINGS
The above and other objects and advantages of the invention will become readily apparent to those skilled in the art from reading the following descriptions of several embodiments of the invention when considered in the light of the accompanying drawings in which:
FIG. 1 is a block diagram of an HVAC system with two parallel switched evaporators according to the prior art;
FIG. 2 is a block diagram of an HVAC system with a combined component including an accumulator and an internal heat exchanger and two double connection blocks according to an embodiment of the invention;
FIG. 3
a is a perspective view of a branch portion of the refrigerant line illustrated in FIG. 1 with two three-way screwing points located on the refrigerant line;
FIG. 3
b is a perspective view of a branch portion of the refrigerant line illustrated in FIG. 1 with one screwing point located on the refrigerant line;
FIG. 4
a is a perspective view of the combined component comprising an accumulator and an internal heat exchanger illustrated in FIG. 2 including a manifold with double connection elements and screwing points arranged opposite in parallel;
FIG. 4
b is a perspective view of the combined component of accumulator and internal heat exchanger illustrated in FIG. 2 including a manifold with double connection elements and screwing points arranged one above another;
FIGS. 5
a-5f are detailed views of the manifold with connections placed opposite to each other illustrated in FIG. 4a; and
FIGS. 6
a-6f are detailed views of the manifold with connections placed one above another illustrated in FIG. 4b.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
The following detailed description and appended drawings describe and illustrate various exemplary embodiments of the invention. The description and drawings serve to enable one skilled in the art to make and use the invention, and are not intended to limit the scope of the invention in any manner.
The block diagram of FIG. 1 shows a prior art HVAC usable to condition air in a vehicle. Such an HVAC has a refrigerant circuit system 1 employing a suitable refrigerant. From a compressor 2 the refrigerant flows through the refrigerant line 3 on the high-pressure side to a gas cooler 4, where the refrigerant is cooled by an environmental air flow. Then the refrigerant flows over the high-pressure entrance 5 into the internal heat exchanger 6 and after having passed the internal heat exchanger 6, over a high-pressure exit 7 to a manifold connection 8. The manifold connection 8 is placed on the refrigerant line 3, whereby the manifold 9 established as three-way screwing point divides the refrigerant line 3 into two branches 10, 11, which run parallel to each other. In each of the branches 10, 11, first, an expansion member 12, 13, respectively, is disposed downstream into which after having passed the manifold 9, the refrigerant flows. In both branches 10, 11 of the refrigerant line 3, the expanding refrigerant is directed to an evaporator 14, 15. Both branches 10, 11 of the refrigerant line 3 then lead from each of the evaporators 14, 15 over two different entrances 16, 17 into a collector 18 or accumulator, where the refrigerant is intermediately stored, before it can flow over the low-pressure entrance 19 into the internal heat exchanger 6 and from there over the low-pressure exit 20 into the compressor 2 again.
FIG. 2 shows a block diagram of an HVAC which is usable to condition air in a vehicle according to the present invention. The HVAC is provided with a refrigerant circuit system 21 employing a suitable refrigerant. From a compressor 22 the refrigerant flows through the refrigerant line 23 on the high-pressure side to a gas cooler 24, where the refrigerant is cooled by an environmental air flow. Then the refrigerant flows over the high-pressure entrance 25 into the internal heat exchanger 26, which is part of the combined component 27 which includes a accumulator 28 or accumulator and the internal heat exchanger 26. At a manifold 29, which includes two double connection elements 30, 31, the high-pressure exit of the internal heat exchanger 26 is divided into two single high-pressure exits 32, 33, which lead to two parallel branches 34, 35 of the refrigerant line 23. The first high-pressure exit 32 leading out of the internal heat exchanger 26 leads over the double connection element 30 into the first branch 34 of the refrigerant line 23. The second high-pressure exit 33 leading out of the internal heat exchanger 26 leads over the second double connection element 31 into the second branch 35 of the refrigerant line 23. In each of the branches 34, 35, the refrigerant is led to an expansion member 36, 37, respectively. From the expansion members 36, 37 the expanded refrigerant reaches a first evaporator 38 and a second evaporator 39, respectively. From the parallel switched evaporators 38, 39 the refrigerant line 23 again leads to the double connection elements 30, 31 of the manifold 29, respectively. Over the first low-pressure entrance 40 at the first double connection element 30 and over the second entrance 41 at the second double connection element 31, the refrigerant line 23 leads the refrigerant into the accumulator 28 of the combined component 27 and over the low-pressure exit 42 the refrigerant can reach the compressor 22 again so that the refrigerant circuit system 21 is closed.
In FIG. 3a, a branch portion of the refrigerant line 3 according to prior art is shown, which provides the connection of the collector 18 and the internal heat exchanger 6, as well as to the parallel switched evaporators 14, 15 and the expansion members 12, 13 in both branches 10, 11 of the refrigerant line 3. Downstream of the high-pressure exit 7 of the internal heat exchanger 6, the manifold 9 that is established as a first three-way screwing point is disposed. The connection of the manifold 9 to the high-pressure exit 7 of the internal heat exchanger 6 is made through the refrigerant line 3 over the manifold connection 8. On the manifold 9 there is a screwing point 44. The manifold 9, as is seen in FIG. 3a, divides the refrigerant line 3 into the first branch 10 and the second branch 11. Both branches 10, 11 of the refrigerant line 3 end in a second three-way screwing point leading to the manifold 43. From the manifold 43 the re-united refrigerant line 3 leads into an entrance of the collector 18. From the collector 18, another portion of the refrigerant line 3 leads over the low-pressure entrance 19 into the internal heat exchanger 6. As shown in FIG. 3a, in this branching portion six screwing points 44 are used, whereby screwing points are used at each of the manifolds 9, 43 on the refrigerant line 3. This requires one additional screwing process on each the high-pressure side and the low-pressure side.
In FIG. 3b, another embodiment of the branching portion of the refrigerant line 3 according to the prior art is shown. In this embodiment, the branching portion facilitates the connection between the collector 18 and the internal heat exchanger 6, as well as between the parallel switched evaporators and expansion members in both branches 10, 11.
In this embodiment, as opposed to the embodiment in FIG. 3a, three of two screwing points 44 are established directly on the collector 18. Both branches 10, 11 of the refrigerant line 3 lead to the two different entrances 16, 17 to the collector 18. For fastening of the refrigerant line 3 to the entrances 16, 17, two of the three screwing points 44 on the collector 18 are provided. Also, the connection line from the collector 18 to the low-pressure entrance 19 of the internal heat exchanger 6 starts, for which another of the three screwing points 44 at the collector 18 is provided. Also in this embodiment of the branching portion, which also corresponds to the arrangement in the block diagram according to FIG. 1, six screwing points 44 altogether are required, whereby one screwing point 44 is placed on the manifold 9 on the refrigerant line 3.
FIG. 4
a shows the combined component 27 including the accumulator 28 and the internal heat exchanger 26 including the manifold 29 which provided with double connection elements 30, 31 that are arranged in parallel opposite to each other and with screwing points 44. The manifold 29 connects the combined component 27 to the two branches 34, 35 which are switched in parallel to each other from the refrigerant line 23. The second branch 34 of the refrigerant line 23 starts at the first high-pressure exit 32 and ends at the first low-pressure entrance 40. Fastening of the first branch 34 of the refrigerant line 23 to the high-pressure exit 32 and the first low-pressure entrance 40 is facilitated over the first double connection element 30. Fastening of the second branch 35 of the refrigerant line 23 to the second high-pressure exit 33 and to the second low-pressure entrance 41 is facilitated over the second double connection element 31. The double connection elements 30, 31, according to FIG. 4a, include one screw for the screwing point 44. Due to the use of the double connection elements 30, 31 the number of screwing points 44 can be reduced from six as required by prior art according systems as shown in FIG. 3a and FIG. 3b to two as shown in FIG. 4a.
FIG. 4
b shows the combined component 27 including the accumulator 28 and the internal heat exchanger 26 including the manifold 29 in a similar arrangement as in FIG. 4a, but wherein the double connection elements 30, 31 and the two screwing points 44 are arranged in parallel above each other on one side of the combined component 27 rather than in parallel opposite to each other as shown in FIG. 4a.
Due to the arrangements of the invention according to FIGS. 4a and 4b, the number of screwing points 44 is reduced to two but further, compared with prior art as shown in FIGS. 3a and 3b, interconnection of the refrigerant line 3 is substantially simplified.
FIG. 5 shows a detailed view of the manifold 29 with connections in parallel opposite to each other as shown in FIG. 4a, without the double connection elements 30, 31 shown. The manifold 29 as a substantially rectangular placed-on body arranged on a cover 45 of the combined component 27 including the internal heat exchanger 26 and the accumulator 28. FIG. 5a shows a side view of the manifold 29, which in this view appears as a rectangular, centrally positioned body placed on the cover 45. Along a central cylinder axis 46 of the combined component 27, the axis 46 running perpendicularly to a circular cover plate 47 of the cover 45, the right-side side view, according to FIG. 5a, is substantially symmetrical.
FIG. 5
b shows a top view of the cover plate 47. Two longitudinal edges 48 of the manifold 29 run parallel, on both sides substantially equally distanced to a mirror symmetry axis 49 of the cover plate 47. An inner edge 50 of the manifold 29 runs perpendicular to both longitudinal edges 48 of the manifold 29 and to the mirror symmetry axis 49 of the cover plate 47, wherein the mirror symmetry axis 49 intersects the inner edge 50 of the manifold 29 at the center. An outer edge 51 of the manifold 29 is rounded in such a form that, as shown in the view in FIG. 5b, the outer edge 51 is congruent to a cover edge 52. As shown in FIG. 5b, the length of the longitudinal edges 48 of the manifold 29 is longer than a radius of the cover 45, but shorter than a diameter of the cover 45. The manifold 29 is arranged asymmetrically with respect to an axis 53 of the cover plate 47, the axis 53 being perpendicular to the mirror symmetry axis 49.
FIG. 5
c shows a front view of the manifold 29. As shown, the manifold 29 on a longitudinal side surface 54 is provided with a central, small circular screw hole 55 and on both sides thereof, two bigger circular holes 56, 57, wherein the low-pressure entrance hole 56 is on the one side and the high-pressure exit hole 57 is on the other side, the centers of which are on a common horizontal axis 58. The smaller central screw hole 55 establishes the screwing point 44 of a double connection element 30, 31. The wider low-pressure entrance hole 56, positioned approximately in the central region of the cover 45, serves as the entrance hole for the refrigerant at low pressure. The high-pressure exit hole 57, located in the edge region of the cover 45, serves as an exit hole for the refrigerant from the internal heat exchanger 26 at high pressure.
FIG. 5
d and FIG. 5e, taken along the cutting planes A-A and B-B in FIG. 5c, respectively, show sections along the cutting plane A-A and B-B, respectively, of the connection block seen in a direction parallel to the cylinder axis 46 of the combined component 27. As shown in FIG. 5d, each of the longitudinal side surfaces includes a low-pressure entrance hole 56.1, 56.2 and a high-pressure exit hole 57.1, 57.2. The sectional view in FIG. 5d also shows an internal low-pressure entrance manifold 59 and an internal high-pressure exit manifold 60. The inner low-pressure manifold 59 facilitates the connection of the two low-pressure entrance holes 56.1, 56.2 to the accumulator 28 of the combined component 27. In the center of a hollow channel 61.1, which extends from the first low-pressure entrance hole 56.1 to the second low-pressure entrance hole 56.2, a fusion channel 62 is arranged perpendicular to the hollow channel 61.1, in such a way that refrigerant flowing in from the low-pressure entrance holes 56.1, 56.2 is brought together in the fusion channel 62.
The inner high-pressure exit manifold 60 facilitates the connection of the two high-pressure exit holes 57.1, 57.2 to the internal heat exchanger 26 of the combined component 27. In the center of the hollow channel 61.2, which extends from the first high-pressure exit hole 57.1 to the second high-pressure exit hole 57.2, there is a circular hole of the connection channel 63 which runs perpendicular to the hollow channel 61.2, wherein the circular hole leads to the pipe of the internal heat exchanger 26.
The T-shaped arrangement of the internal low-pressure entrance manifold 59 is shown in FIG. 5e by a sectional view along the cutting plane B-B according to FIG. 5c. The hollow channel 61.1, which extends from the first low-pressure entrance hole 56.1 up to the second low-pressure entrance hole 56.2, is divided in the center by the fusion channel 62, which is positioned perpendicular to the hollow channel 61.1. The fusion channel extends from the hollow channel 61.1 through the interior of the cover 45 up to an inner surface of the cover 45.
FIG. 5
f shows an isometric representation of the cover 45 with a manifold 29, which on each of both longitudinal side surfaces 54 is provided with three different holes 55, 56, 57. The manifold 29 is substantially rectangular, with the exception of an edge side surface 64 at the outer edge 51 of the manifold 29, which is curved like the cover edge 52.
A detailed view of the manifold 29 with connections which are arranged parallel above another as shown in FIG. 4b is shown in FIG. 6. The manifold 29 is a substantially rectangular body placed on a cover 45 of the combined component 27 including the internal heat exchanger 26 and the accumulator 28. FIG. 6a shows a side view of the manifold 29, which in this view appears as a substantially rectangular body disposed off center from the cover 45. The connection block 29 of FIG. 6 is narrower and higher than the connection block 29 shown in FIG. 5.
FIG. 6
b shows a top view of a cover plate 47. Both longitudinal edges 65, 66 of the manifold 29 run parallel to an axis 68 of the cover 45. An inner edge 67 of the manifold 29 runs perpendicular to both longitudinal edges 65, 66 and the axis 68 of the cover 45. The axis 68 of the cover 45 intersects the inner edge 67 outside of the center of the inner edge 67. An outer edge 69 of the manifold 29, however, is curved in such a form that, as shown in the top view in FIG. 6b, the outer edge 69 is congruent to a cover edge 52. According to FIG. 6b, the length of the longitudinal edges 65, 66 is longer than a radius of the cover 45, but shorter than a diameter of the cover 45.
FIG. 6
c shows a front view of the manifold 29 according to this embodiment of the invention. The manifold 29 on a longitudinal side surface 70 includes two central, small circular screw holes 71 formed above each other and on either side of two wider circular holes 72, 73, which are formed above each other. The wider holes 72, 73 formed above each other, on the one side, being low-pressure entrance holes 72 and, on the other side, high-pressure exit holes 73. Centers of the three upper circular holes 71, 72, 73 are located on a common upper horizontal axis 74 and centers of the three lower circular holes 71, 72, 73 are located on a lower horizontal axis 75, which is parallel to the upper horizontal axis 74. The smaller central screw holes 71 establish the screwing point 44 of double connection elements 30, 31. The bigger low-pressure entrance holes 72 formed above each other, which are formed approximately in the central region of the cover 45, serve as entrance holes for the refrigerant at low pressure. Both high-pressure exit holes 73 formed above each other, which are located in the edge region of the cover 45, serve as exit holes for the refrigerant from the internal heat exchanger 26 at high pressure.
Referring to the identification of the cutting planes A-A and B-B, respectively, of FIG. 6c, in FIG. 6d a section along the cutting plane A-A of the connection block 29 is shown in direction parallel to the cylinder axis 46 of the combined component 27. As shown in FIG. 6d, only on the longitudinal side surface 70 below the longitudinal edge 65 are holes 71, 72, 73. The sectional view in FIG. 6d shows an internal low-pressure entrance manifold 76 and an internal high-pressure exit manifold 77. The inner low-pressure manifold 76 connects the two low-pressure entrance holes 72 to the accumulator 28 of the combined component 27. Short entrance channels 78 lead into a fusion channel 79, which is positioned perpendicular to the entrance channels 78, in such a way that refrigerant flowing in from both low-pressure entrance holes 72 is brought together in the fusion channel 79.
The inner high-pressure exit manifold 77 connects the two high-pressure exit holes 73 to the internal heat exchanger 26 of the combined component 27. The short entrance channels 78 lead into a connection channel 80 which is positioned perpendicular to the entrance channels 78.
The F-shaped arrangement of the internal low-pressure entrance manifold 76 is shown in FIG. 6e as a sectional view along the cutting plane B-B shown in FIG. 6c. The entrance channels 78 lead into the connection channel 80, which is aligned perpendicular to the entrance channels 78, wherein the connection channel 80 extends through an interior of the cover 45 up to an inner surface of the cover 45.
FIG. 6
f shows an isometric representation of the cover 45 with a manifold 29 which is provided with holes 71, 72, 73 only on the longitudinal side surface 70 below the longitudinal edge. The manifold 29 is substantially rectangular, with the exception of the edge side surface 64 below the outer edge 69 of the manifold 29, the edge side surface 64 being curved like the cover edge 52.
From the foregoing description, one ordinarily skilled in the art can easily ascertain the essential characteristics of this invention and, without departing from the spirit and scope thereof, can make various changes and modifications to the invention to adapt it to various usages and conditions.
Patent Application
20080034787
