Patient heat exchange system with two and only two fluid loops

Abstract

A heat exchange system for exchanging heat with working fluid from an intravascular heat exchange catheter or an external heat exchange pad includes a working fluid that circulates between the catheter or pad and a fluid cassette, and a refrigerant system that flows against the outer sides of cold plates between which the cassette is disposed.

Claims

1. A heat exchange system for exchanging heat with working fluid from an intravascular heat exchange catheter or an external heal exchange pad, comprising: a working fluid circuit configured for circulating working fluid between a fluid cassette and the catheter or pad; and a refrigerant circuit configured for circulating refrigerant between a compressor and sides of heat exchange plates between which the cassette is disposable, wherein each heat exchange plate communicates with a source of refrigerant, wherein a cassette slot is defined between the heat exchange plates for receiving the fluid cassette, wherein the heat exchange plates abut each other along left and right side walls, wherein respective vertically elongated cassette frame receptacles are located immediately inboard of the respective left and right side walls with the slot extending between the side walls and terminating at the receptacles, the frame receptacles being wider than the slot and extending past opposed sides of the slot; wherein a chamfer is formed in at least one of the heat exchange plates and is configured to accommodate ballooning in the fluid cassette.

2. The system of claim 1, wherein the working fluid circuit is configured for circulating working fluid between the fluid cassette and the catheter.

3. The system of claim 1, wherein the working fluid circuit is configured for circulating working fluid between the fluid cassette and the pad.

4. The system of claim 1, wherein at least one heat exchange plate is formed with a serpentine passageway through which the refrigerant can flow.

5. The system of claim 1, wherein a distance between the heat exchange plates is between twenty nine mils and thirty one mils (0.029-0.031).

6. The system of claim 1, wherein the heat exchange plates are square.

7. The heat exchange system of claim 1, wherein each heat exchange plate is associated with its own respective refrigerant inlet and outlet tubes through which each heat exchange plate communicates with a source of refrigerant.

8. The system of claim 1, wherein the frame receptacles extend laterally beyond opposed first and second edges of the slot.

9. A system comprising: two heat transfer plates parallel to each other and defining a slot between them configured for receiving a working fluid cassette through which working fluid flows to and from an intravascular catheter in a working fluid circuit wherein each heat transfer plate communicates with a source of refrigerant; wherein the heat transfer plates abut each other along left and right side walls and respective vertically elongated cassette frame receptacles are located immediately inboard of the respective side walls and are formed in each plate with the slot extending between the side walls and terminating at the receptacles, the frame receptacles being wider than the slot and wherein a chamfer is formed in at least one of the heat transfer plates and is configured to accommodate ballooning in the working fluid cassette.

10. The system of claim 9, wherein a distance between the heat transfer plates is less than forty mils (0.040).

11. The system of claim 9, wherein a distance between the heat transfer plates is between twenty nine mils and thirty one mils (0.029-0.031).

12. The system of claim 9, wherein the heat transfer plates are square.

13. The system of claim 9, wherein at least one heat transfer plate is formed with a serpentine passageway through which the refrigerant flows.

14. The system of claim 9, wherein each heat transfer plate is associated with its own respective refrigerant inlet and outlet tubes through which each heat transfer plate communicates with a source of refrigerant.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a schematic view of a non-limiting system in accordance with the present invention;

(2) FIG. 2 is a perspective view of an example working fluid cassette holder portion of a heat exchange system;

(3) FIG. 3 is a perspective view of one half of the cassette holder shown in FIG. 2, with the opaque metal inner surface shown in transparency to reveal the serpentine refrigerant passageway;

(4) FIG. 4 is a perspective view of an example working fluid cassette configured to engage the cassette holder shown in FIGS. 2 and 3;

(5) FIG. 4A is similar to FIG. 4, showing the inlet and outlet tubes extending from the top to the bottom of the membrane assembly;

(6) FIG. 5 is a close up perspective view of the cassette shown in FIG. 4, illustrating an inlet tube extending partially down into the stretched membrane chamber, it being understood that an opposed outlet tube may be similarly disposed on the opposite side of the cartridge and that both the inlet and outlet tubes may extend any length down their respective sides in the cassette;

(7) FIG. 6 is a perspective view of an alternate cassette in which the inlet and outlet tubes are formed in the frame of the cassette, with portions broken away for clarity;

(8) FIG. 7 is a view in partial cross-section as seen along the line 7-7 in FIG. 6, with portions broken away for clarity, and assuming the cassette is engaged between the cold plates; and

(9) FIG. 8 is a schematic diagram of a refrigerant-working fluid system.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

(10) Referring initially to FIG. 1, in accordance with present principles, a system 10 may include an intravascular heat exchange catheter 12 controlled by a control system 14 to induce control patient temperature, e.g., to prevent the patient 16 from becoming febrile or to induce therapeutic hypothermia in the patient 16. In the catheter, working fluid (also referred to as coolant) such as but not limited to saline circulates (typically under the influence of a pump in the controller) in a closed loop from the control system 14, through a fluid supply line L1, through the catheter 12, and back to the system 14 through a fluid return line L2, such that no coolant enters the body. While certain preferred catheters are disclosed below, it is to be understood that other catheters can be used in accordance with present principles, including, without limitation, any of the catheters disclosed above or in the following U.S. patents, all incorporated herein by reference: U.S. Pat. Nos. 5,486,208, 5,837,003, 6,110,168, 6,149,673, 6,149,676, 6,231,594, 6,264,679, 6,306,161, 6,235,048, 6,238,428, 6,245,095, 6,251,129, 6,251,130, 6,254,626, 6,261,312, 6,312,452, 6,325,818, 6,409,747, 6,368,304, 6,338,727, 6,299,599, 6,287,326, 6,126,684. The catheter 12 may be placed in the venous system, e.g., in the superior or inferior vena cava.

(11) Instead of or in addition to the catheter 12, the system 10 may include one or more pads 18 that are positioned against the external skin of the patient 16 (only one pad 18 shown for clarity). The pad 18 may be, without limitation, any one of the pads disclosed in the external pad patents. The temperature of the pad 18 can be controlled by a pad control system 20 in accordance with principles set forth in the external pad patents to exchange heat with the patient 16, including to induce therapeutic mild or moderate hypothermia in the patient in response to the patient presenting with, e.g., cardiac arrest, myocardial infarction, stroke, high intracranial pressure, traumatic brain injury, or other malady the effects of which can be ameliorated by hypothermia. The pad 18 may receive working fluid from the system 20 through a fluid supply line L3, and return working fluid to the system 20 through a fluid return line L4. Note that in some embodiments, the systems 14,20 are established in a single assembly.

(12) To cool the patient while awaiting engagement of the catheter 12 and/or pad 18 with the patient, cold fluid 22 in a cold fluid source 24 may be injected into the patient and in particular into the patient's venous system through a pathway 26. Without limitation, the pathway 26 may an IV line, the source 24 may be an IV bag, and the fluid 22 may be chilled saline, e.g., saline at the freezing point or slightly warmer. Or, the source may be a syringe, and the saline can be injected directly into the bloodstream of the patient.

(13) Now referring to FIG. 2, a portion of either of the heat exchangers in the control systems 14,20 is shown which includes at least two cold plates 30, 32 defining a cassette slot 34 between them. In one embodiment, the width W of the slot 34 is less than forty mils (0.040), and may be between twenty nine mils and thirty one mils (0.029-0.031) or may have a nominal slot width of 0.035. In a specific example the width W may be thirty mils. In other embodiments, when a disposable heat exchange bag with serpentine channels is used, a larger gap between the cold plates may be used, e.g., 0.060-0.120 and more preferably 0.080 to promote pumping saline through the bag without excessive backpressure.

(14) The cold plates 30,32 may be made of metal, and can be rectilinear as shown and indeed may be nearly square. The cold plates 30, 32 may abut each other along left and right side walls 36, with elongated vertical cassette frame receptacles R1 and R2 being located immediately inboard of the respective side walls 36 and with the slot 34 extending between the walls 36 and terminating at the receptacles R1, R2 as shown. The frame receptacles R1, R2 are wider than the slot 36.

(15) In the example shown, refrigerant inlet and outlet tubes 38,40 extend through at least one of the cold plates 32 to communicate refrigerant from a compressor into a refrigerant passageway in the cold plate. Each cold plate may have its own refrigerant inlet and outlet tubes, or, in the embodiment shown, only one cold plate may be formed with refrigerant inlet and outlet tubes and the other cold plate either thermally coupled to the cold plate in which the refrigerant flows and/or receiving refrigerant from the other cold plate through passageways formed through one or both of the side walls 36.

(16) FIG. 3 shows details of an example cold plate 32 looking at the inner surface in transparency, it being understood that the inner surface typically is metal and that the serpentine refrigerant passageway 42 shown in FIG. 3 typically would not be visible to the human eye. In any case, the example refrigerant passageway that fluidly connects the refrigerant inlet 38 to the refrigerant outlet 40 may be serpentine-shaped as shown, or may be some other shape or pattern such as a herringbone pattern a wave pattern, etc. Alternatively, parallel channel passages may be used. For instance, ten one-inch wide channels may be formed in parallel, thereby achieving a 1010 surface area.

(17) FIG. 4 shows an example working fluid cassette 50 according to present principles. The cassette 50 is configured to fit snugly into the slot 34 and cassette frame receptacles R1, R2 defined between the cold plates 30, 32. Working fluid such as saline from a patient-engageable heat exchange member such as the catheter 12 or pad 18 flows through the cassette 50 in operation, with the working fluid exchanging heat with the refrigerant in the cold plates. In example embodiments, the cassette 50 is a low cost single-use disposable item that can contain, e.g., sterile saline which circulates through the catheter 12. The cassette may be placed by a medical caregiver in the slot 34 between the cold plates 30, 32 and the membrane portion which defines a space or working fluid chamber through which the example saline flows inflates when the working fluid flows through it, achieving thermal contact with the cold plates 30, 32.

(18) In the example shown, the cassette 50 includes a frame 52 defining a periphery and a preferably rectilinear opening bounded as shown on at least three sides by the periphery of the frame. In the non-limiting example shown, the frame includes an elongated parallelepiped-shaped top rail 53 and elongated parallelepiped-shaped left and right side rails 54 parallel to each other and perpendicular to the top rail 32. The example frame 52 has no bottom rail opposite the top rail. In any case, the example frame 52 is rectilinear and is configured for being closely received between the two cold plates 30,32, with the side rails 54 slidably engageable with the frame receptacles R1, R2 between the cold plates 30, 32 and with the below-described membrane assembly passed through the slot 36 to be in close juxtaposition with the refrigerant channels in the cold plates.

(19) In cross-references to FIGS. 4 and 5, the frame, in the example shown, the top rail 53 thereof, is formed with a fluid inlet 56 in which an inlet tube 58 has been disposed and a fluid outlet 60 in which an outlet tube 62 has been disposed. Both the inlet and outlet establish respective fluid passageways through the frame into the opening. The inlet and outlet tubes 58, 62 may be engaged with the fluid return and supply lines L3, L4 that are associated with the catheter 12. The tubes 58,62 may terminate at just below the top rail 53 (FIG. 4), or they may extend any desired length down to the bottom of the assembly, i.e., the tubes 58,62 may extend almost the entire length of the left and right side rails 54, ending just above the below-described bottom seam of the membrane assembly (FIG. 4A).

(20) Indeed, a polymeric membrane assembly 64 is connected to the frame 52, blocking the opening that is bounded on three sides by the frame as shown. The membrane assembly includes a first membrane 66 that is parallel to and closely spaced from a second membrane 68, leaving a space there between which establishes a working fluid chamber. The fluid inlet 56 and fluid outlet 60 communicate with the space between the membranes 66,68. At least one and preferably both of the membranes 66,68 are disposed in tension in the opening. The space between the membranes is expandable when filled with working fluid.

(21) In one example, each membrane is no more than two mils (0.002) thick and more preferably is between one mil and two mils in thickness (0.001-0.002), inclusive. The example preferred membranes 66, 68 are co-extensive with the opening and like the opening are more or less square, with the length of top and bottom edges of the example membranes being approximately equal (within 10% and more preferably within 5%) of the lengths of the left and right edges of the membranes. Thus, the working fluid chamber between the membranes is also rectilinear and in the preferred embodiment no obstructions exist between the membranes, meaning the working fluid chamber is a complete rectilinear, more or less square chamber.

(22) Owing to the thinness of the membranes 66,68 and the closeness of the cold plates 30,32 to each other and to the membrane assembly between them when the cassette is engaged with the cold plates, the system shown in the figures affords low impedance of heat transfer between the refrigerant circulating in the cold plates and the working fluid circulating between the membranes 66, 68. The working fluid chamber between the membranes inflates due to backpressure generated by working fluid flow, eliminating or reducing the need for a moving mechanism in the cold plates. Moreover, the narrow slot 34 between the two cold plates provides better heat transfer by reducing the conductive path length between the cold plates and the working fluid. The frame allows for ease of handling, such as insertion and removal of the cassette with/from the cold plates.

(23) With respect to the example working fluid chamber between the membranes 66, 68 having a width-to-length aspect ratio near 1:1 (i.e., square or nearly so), the amount of backpressure required to induce working fluid flow through heat exchanger is reduced compared to a less square configuration. This reduces the amount of work that a working fluid pump must perform, which is desirable for two reasons. One, since the pump may be disposable, lower performance requirements translate into a lower cost disposable and quieter system. For instance, peristaltic roller pumps offer quiet operation and a low-cost disposable element, but operate most efficiently when only modest pressures are required. Two, lowering the working fluid pump work reduces the amount of heat transferred into the working fluid by the pump itself. Also, a low width/length aspect ratio results in slower working fluid velocity which reduces amount of mixing, but this otherwise desirable (from a heat exchange standpoint) effect is negligible in the present example system since the Reynolds numbers are typically <1000, suggesting a laminar flow regime. Furthermore, a low width/length aspect ratio significantly reduces the number of bends (or corners) in the fluid flow path. These bends are areas of mixing for the fluid which promotes heat transfer. Without them, a fluid boundary layer builds up. However, this effect is offset herein by maintaining a narrow slot between the cold plates. This way the primary heat transfer mechanism is by conduction, but the conduction path length (and therefore boundary layer) is small, resulting in a relatively high rate of heat transfer.

(24) In preferred examples, the membranes 66,68 are stretched under tension during assembly to the frame. This tension can be maintained over the shelf life of the product. Pretensioning minimizes wrinkles in material, which is beneficial because wrinkles can impede working fluid flow and create air gaps which reduce heat transfer between the working fluid and cold plates. Wrinkles can also complicate insertion of the membrane assembly into the narrow slot 34.

(25) To establish pre-tensioning of the membranes, the frame may be made in halves and posts such as threaded fasteners 70 (FIG. 5) can extend transversely to one half of the frame, with the membranes 66, 68 being stretched over the posts and holes made in the membranes to receive the posts. The other half of the frame is then positioned to sandwich a rectilinear border portion 74 (only the innermost portion of which is shown in FIG. 5) of the membrane assembly between the frame halves, and a closure such as respective nuts 72 engaged with the posts 70 to hold the frame halves together with the membrane assembly held in tension between the frame halves. FIG. 4 shows that the working fluid chamber is closed off at the bottom by a bottom seam 74A of the membrane assembly, which is part of the border portion 74.

(26) In the border portion 74, at least one and preferably more layers of polymer film may be used to reinforce the membranes 66,68 to establish welded seams through which (at the sides of the membrane assembly) the post holes are formed, allowing for easier fabrication. By placing reinforcing layers on the border portion 74 only, the central window of the membrane assembly consists only of a single thin layer membrane between the working fluid and one of the cold plates 30,32 to minimize impeding heat transfer. A die-cut reinforcement layer may be used which reinforces the entire perimeter with one piece of material.

(27) In some examples, the polymer membranes 66,68 are highly stretchable, at least greater than 25% elongation. This allows the membranes to change from the empty flat state shown in FIGS. 4 and 5 to an inflated shape (within the slot 34 between the cold plates) without wrinkling. It also allows the membranes to easily conform to features on the faces of the cold plates.

(28) Additionally, the membranes may be made of a material which can also be made into tubing. Tubes such as the inlet and outlet tubes 58, 62 shown in FIG. 4 can then be thermally welded (e.g., using RF sealing) to the membranes, which is more reliable and quicker than adhesive bonding. The membranes 66, 68 need not provide their own lateral support because the cold plates 32, 34 and frame provide the support for the inflated membrane assembly, allowing it to withstand the pressure generated as a result of working fluid flowing through between the membranes. Structural features may be located on the cold plates to optimize heat transfer. This can be economically advantageous because the cold plates are reusable components. Manifolds can be cut into the cold plates to even out the distribution of saline flow.

(29) FIGS. 6 and 7 show that alternatively, a working fluid inlet 80 may be formed in the left rail of a frame 82 holding a membrane assembly 84 in tension. It is to be understood that a working fluid outlet may be formed in the right rail of the frame 82. The inlet 80 and outlet may extend almost the entire length of the rail if desired or may extend only part way down the rail. In any case one or more lateral channels 86 extend from the inlet 80 to the working fluid chamber 88 of the membrane assembly 84 to establish fluid communication between the inlet (and outlet) of the frame 82 and the working fluid chamber. If desired, the cold plates 30,32 may be formed with a chamfer 90 at the start of the slot 92 in which the membrane assembly 84 is disposed, with a complementarily shaped chamfer 94 being formed in the rail of the frame 82, to accommodate any ballooning of the membrane assembly 84 at the frame/membrane interface as the saline flows out of the frame into the membrane assembly.

(30) FIG. 8 shows an example system 100 that may use the fluid cassette 50 between the cold plates 30, 32. The system 100 may be an embodiment of either system 14,20 shown in FIG. 1, for example. Refrigerant circulates from a compressor 102 through a refrigerant supply line 104 to at least one of the cold plates as shown. In the embodiment shown, the refrigerant circulates through a cold plate bottom coupler 106 from the first cold plate 30 to the second cold plate 32 and back to the compressor 102 through a refrigerant return line 108. In other embodiments the refrigerant may flow only through the first cold plate 30 which, owing to thermal coupling through the bottom coupler 106 with the second cold plate 32, equalizes the temperature of the second cold plate 32 with the temperature of the first cold plate 30. Yet again, separate refrigerant supply and return lines apart from the lines 104,108 may be provided between the compressor 102 (or indeed a second compressor) and the second cold plate 32.

(31) Thus, as shown in FIG. 8 only two fluid loopsrefrigerant and working fluidneed be used. The prime mover of the heat exchange in the system 100 is the refrigerant loop with compressor, and it directly exchanges heat with the end use fluid system, the working fluid loop.

(32) While the particular PATIENT HEAT EXCHANGE SYSTEM WITH TWO AND ONLY TWO FLUID LOOPS is herein shown and described in detail, the scope of the present invention is to be limited by nothing other than the appended claims.