Measurement of the NCG concentration in a steam sterilizer

Abstract

A method and system for determining steam sterilant quality of a steam sterilizer where the steam sterilant comprises non-condensable gas(es).

Claims

1. Method for determining steam sterilant quality of a steam sterilizer, the method comprising: a) providing within the sterilizer a challenge device comprising a tube having a bore, the bore of the tube defining a free space which is open at one end for the entry of steam sterilant and closed at the other end; at least one thermal load having a predetermined heat capacity located around the tube, wherein the at least one thermal load contacts directly or indirectly the tube over a contact surface area and there is a predetermined thermal resistance between the tube and the at least one thermal load; a temperature sensor adapted to measure the temperature of the at least one thermal load; as well as a pressure sensor adapted to measure pressure in the steam sterilizer and/or a temperature sensor adapted to measure the temperature in the steam sterilizer; wherein the challenge device is configured and arranged such that, in use, condensate will flow out of the bore; b) allowing steam sterilant comprising non-condensable gas(es) to interact with the challenge device; c) measuring over time the temperature of the at least one thermal load and the pressure and/or temperature in the sterilizer; d) calculating the quantity of non-condensable gas(es) collected in the tube during a selected time interval t on the basis of the temperature of the at least one thermal load over the selected time interval t, the pressure and/or temperature in the sterilizer over the selected time interval t, the thermal resistance between the tube and the at least one thermal load, the heat capacity of the at least one thermal load and the geometry of the tube; e) calculating the quantity of steam condensed in the tube during the selected time interval t on the basis of the heat capacity of the at least one thermal load, the temperature of the at least one thermal load over the selected time interval t, and the specific condensation heat of the steam, wherein the value of specific condensation heat of the steam is either determined on the basis of the measured pressure and/or temperature over time in the sterilizer or used as a constant value independent of temperature dependency; and f) determining the steam sterilant quality on the basis of the quantity of non-condensable gas(es) collected in the tube during the selected time interval t and the quantity of steam condensed in the tube during the selected time interval t.

2. The method of claim 1, wherein the quantity of non-condensable gas(es) collected in the tube during the selected time interval t is calculated in terms of volume (V.sub.NCG) and/or mass (m.sub.NCG).

3. The method of claim 1, wherein the quantity of steam condensed in the tube during the selected time interval t is calculated in terms of mass (m.sub.steam) and/or volume (V.sub.steam).

4. The method of claim 1, wherein the quality of steam sterilant is represented as a percentage of the ratio of the quantity of non-condensable gas(es) collected in the tube during the selected time interval t and the quantity of steam condensed in the tube during said time interval t, in particular the ratio is selected from the group consisting of V.sub.NCG/m.sub.steam, V.sub.NCG/V.sub.steam, m.sub.NCG/m.sub.steam and m.sub.NCG/V.sub.steam.

5. The method of claim 1, wherein the challenge device comprises a single thermal load, or wherein the challenge device comprises two or more thermal loads and two or more temperature sensors adapted to measure the temperature of each thermal load, in particular two or three thermal loads and two or three temperature sensors, respectively, each temperature sensor adapted to measure the temperature of a thermal load.

6. A system for determining steam sterilant quality of a steam sterilizer where the steam sterilant comprises non-condensable gas(es), the system comprising: a) a challenge device comprising a tube having a bore, the bore of the tube defining a free space which is open at one end for the entry of steam sterilant and closed at the other end; at least one thermal load having a predetermined heat capacity located around the tube, wherein the at least one thermal load contacts directly or indirectly the tube over a contact surface area and there is a predetermined thermal resistance between the tube and the at least one thermal load; a temperature sensor adapted to measure the temperature of the at least one thermal load; as well as a pressure sensor adapted to measure pressure in the steam sterilizer and/or a temperature sensor adapted to measure the temperature in the steam sterilizer; wherein the challenge device is configured and arranged such that, in use, condensate will flow out of the bore; b) at least one data collection unit, the as least one data collection unit configured and arranged, such that, in use, it allows for measuring over time the temperature of the at least one thermal load and, as applicable, the pressure and/or temperature in the sterilizer as well as storing measured data together with their corresponding time stamp; c) at least one data evaluation unit; the at least one data evaluation unit configured and arranged such that, in use, it allows for: i) calculating the quantity of non-condensable gas(es) collected in the tube during a selected time interval t on the basis of the temperature of the at least one thermal load over the selected time interval t, the pressure and/or temperature in the sterilizer over the selected time interval t, the thermal resistance between the tube and the at least one thermal load, the heat capacity of the at least one thermal load and the geometry of the tube; ii) calculating the quantity of steam condensed in the tube during the selected time interval t on the basis of the heat capacity of the at least one thermal load, the temperature of the at least one thermal load over the selected time interval t, and the specific condensation heat of the steam, wherein the value of specific condensation heat of the steam is either determined on the basis of the measured pressure and/or temperature over time in the sterilizer or used as a constant value independent of temperature dependency; and iii) determining the steam sterilant quality on the basis of the quantity of non-condensable gas(es) collected in the tube during the selected time interval t and the quantity of steam condensed in the tube during the selected time interval t.

7. The system of claim 6, wherein the challenge device comprises a single thermal load, or wherein the challenge device comprises two or more thermal loads and two or more temperature sensors adapted to measure the temperature of each thermal load, in particular two or three thermal loads and two or three temperature sensors, respectively, each temperature sensor adapted to measure the temperature of a thermal load.

8. The system of claim 6, wherein the tube has along its length a thermal conductivity of 30 Wm.sup.1K.sup.1 or less; and/or wherein the tube has along its cross-section a thermal conductivity greater than 2 Wm.sup.1K.sup.1; and/or wherein the thermal conductivity along the longtidunal axis of the tube does exceed 120% of the thermal conductivity in a radial direction.

9. The system of claim 6, wherein the tube has a length of 15 cm or less; and/or wherein the tube is a hollow cylinder having a wall thickness of 2 mm or less; and/or wherein the bore of the tube has a bore diameter of between 2 mm and 12 mm; and/or wherein the cross section of the tube has an area of 210 mm.sup.2 or less.

10. The system of claim 6, wherein the tube is made of metal, in particular the tube is a metal tube comprising one or more selected from: stainless steel; non-rusting steel; CrNi-containing steel; titanium; and titanium alloys.

11. The system of claim 6, wherein the at least one thermal load has a shape substantially corresponding to a cylinder with a bore.

12. The system of claim 11, wherein the size and shape of the bore of the at least one thermal load generally corresponds to the outer size and shape of the tube.

13. The system of claim 11, wherein the bore of the at least one thermal load and/or the surface of the bore of the at least one thermal load is shaped such as to intermittently contact the tube.

14. The system of claim 6, wherein a foil or sheet of thermally insulating material is provided between the tube and the at least one load, in particular said foil or sheet comprises a material having a thermal conductivity which is lower than that of the tube.

15. The system of claim 6, wherein the at least one load has a heat capacity at 25 C. of at least 0.5 Jg.sup.1K.sup.1.

Description

BRIEF DESCRIPTION OF FIGURES

(1) FIG. 1 shows a schematic sketch of a challenge device that may be utilized with methods and systems described herein;

(2) FIG. 2 shows a schematic sketch of another challenge device that may be utilized with methods and systems described herein;

(3) FIG. 3 shows a curve of measured parameter for a typical sterilization run using an exemplary challenge device of the type described herein; and

(4) FIG. 4 shows the curve of FIG. 3 including various determined data using exemplary calculations of the type described herein.

(5) FIG. 5 shows a schematic sketch of a system in accordance with an aspect of the present disclosure;

(6) FIG. 6 shows a schematic sketch of another system described herein in accordance with an aspect of the present disclosure;

DETAILED DESCRIPTION

(7) FIG. 1 shows a schematic sketch of a challenge device in cross-section. The challenge device comprises a tube (1) having a bore (2). The bore (2) of the tube (1) defines a free space which is open at the bottom end for the entry of steam sterilant comprising non-condensable gas(es) and closed at the top end and one open end. Since the opening into the bore is located at the bottom of the device, in use, condensate will flow out of the bore. The device further comprises a single thermal load (3) located around the tube (1), wherein a foil (4) is located between the tube and load. There is direct contact between the tube, foil and thermal load, so that the thermal load (3) indirectly contacts the tube over a contact surface area. There is a predetermined (i.e. known or set) thermal resistance from the inner surface of the tube to the inner surface of load (3). The foil is used for specific adjustment of thermal resistance between the tube and the load.

(8) Preferably, the tube material has a thermal conductivity along its length of 30 Wm.sup.1K.sup.1 (Watt per meter Kelvin) or less, more preferably of 25 Wm.sup.1K.sup.1 or less, and most preferably of 20 Wm.sup.1K.sup.1 or less. Thus, such thermal conductivities facilitate minimization or elimination of artefacts due to heat transfer along the length of the tube. It is preferred that tubes have along their cross-section a thermal conductivity greater than 2 Wm.sup.1K.sup.1, more preferably greater than 4 Wm.sup.1K.sup.1. Here, such thermal conductivities favourably facilitate transport the heat generated during condensation to the thermal loads in a radial direction. For tubes made of an isotropic material or an essentially isotropic material (such as a metal) favourably such the tube materials have a thermal conductivity of 30 Wm.sup.1K.sup.1 or less (more favourably of 25 Wm.sup.1K.sup.1 or less, and most favourably of 20 Wm.sup.1K.sup.1 or less) and a thermal conductivity greater than 2 Wm.sup.1K.sup.1 (more favourably greater than 4 Wm.sup.1K.sup.1).

(9) Preferably, the material properties, in particular the thermal conductivity, of tubes are essentially isotropic. It is preferred that the thermal conductivity along the longitudinal axis of the tube does not exceed 120%, preferably 110%, and more preferably 105% of the thermal conductivity in a radial direction.

(10) Desirably tubes may be made of metal. Preferably, metal tubes comprise one or a combination of: stainless steel; non-rusting steel; CrNi-containing steel; titanium; and titanium alloys.

(11) Tubes may favourably have a length of 15 cm or less, more preferably 12 cm or less, even more preferably 10 cm or less. Favourably, tubes are hollow cylinders having a wall thickness of 2 mm or less, preferably of 1.5 mm or less, more preferably of 1 mm or less and most preferably of 0.5 mm or less. Favourably, tubes have a bore diameter of between 2 mm and 12 mm, preferably between 3.5 mm and 10.5 mm, more preferably between 5 mm and 8 mm (inclusive the end points). Tubes inclusive wall thickness and bore may favourably have a cross sectional area of 210 mm.sup.2 or less, more preferably of 170 mm.sup.2 or less, even more preferably of 140 mm.sup.2 or less.

(12) Thermal loads preferably have a large heat capacity of preferably equal to or greater than 0.5 Jg.sup.1K.sup.1 at 25 C., more preferably of equal to or greater than 0.7 Jg.sup.1K.sup.1, even more preferably of equal to or greater than 0.85 Jg.sup.1K.sup.1. An exemplary suitable material for the thermal loads is aluminium.

(13) Load(s) preferably have a shape substantially corresponding to a cylinder with a bore. Desirably the size and shape of the bore of the load(s) generally corresponds to the outer size and shape of the tube. This facilitates the provision of a well-defined heat transfer between the tube and the one or more loads. Preferably, the bore of the one or a plurality of loads and/or the surface of the bore of the one or a plurality of loads may be shaped such as to only intermittently contact the tube. This desirably allows an increased control and optimization of the amount of heat transfer between the tube and the load(s). For example, the surface of the bore of the one or more loads may comprise at least one laterally or longitudinally extending groove, preferably at least two or more laterally and/or longitudinally extending grooves, which are preferably spaced equidistantly from each other. In essence, heat transfer then only takes place at the intermittent contact between the load(s) and the tube where no groove is present.

(14) Alternatively or in addition, a foil or sheet of thermally insulating material may be provided between the tube and the one or more loads. Such a foil or sheet may preferably comprise a material comprises one or a combination of: polyester, polypropylene, polyacrylonitrile, Kapton, polyurethane, polyamide, polyimide, polyether imide, PTFE, polyvinylchloride, polycarbonate, epoxy resin, polymethyl-methacrylate, polyethylene, and polystyrene. The use of such foils or sheets further aids in providing a well-defined heat transfer between the tube and the one or more loads and/or in controlling or optimizing the amount of heat transfer between the tube and the one or more loads. Foils or sheets preferably comprises a material having a thermal conductivity which is lower than that of the tube. Such materials may have a thermal conductivity of 5 Wm.sup.1K.sup.1 or less, more preferably of 1 Wm.sup.1K.sup.1 or less. To adjust thermal coupling between the tube and the one or more loads, foils or sheets may favourably comprise several holes and/or cut-outs.

(15) Returning to FIG. 1, when steam comprising non-condensable gas(es) enters the open bottom end of the bore, part of the steam condenses at the comparably cold inner surface of the tube (1) which allows for the condensate being generated to flow out of the bore. Due to the condensation a certain amount of non-condensable gas(es) is collected at the closed top end of the bore (2) (indicated with NCG in the sketch). Generally, the amount of heat transferred from the bore (2) of the tube (1) to the load (3) is smaller over that portion of the contact surface area between tube and load over which the bore of the tube is in contact with non-condensable gas(es), than steam, since the condensation of the steam provides for an increased energy input into the thermal load due to condensation heat. Thus, the course of the temperature of the thermal load over time provides information about the amount of non-condensable gas(es) versus the amount of condensed steam. This allows for a determination of steam sterilant quality on the basis of the quantity of non-condensable gas(es) and the quantity of condensed steam. The temperature of the thermal load is measured by means of a temperature sensor (5).

(16) The exemplary embodiment shown in FIG. 1 is also provided with a temperature sensor (6) as well as a pressure sensor (7) which allow for the measurement of temperature and pressure, respectively, inside the sterilizer (i.e. measurement of unchallenged temperature and pressure). Favorably challenge devices include both sensors, however it is possible to use just a temperature sensor or alternative just a pressure sensor. If a single sensor is being used desirably it is a pressure sensor, because pressure sensors are typically more precise and have faster response times. The temperature inside the sterilizer can be derived from measured pressure data, and in fact due to the mentioned favorable features of pressure sensor, this derived temperature will allow for more accuracy results. The skilled person knows how to derive temperature from measure pressure data.

(17) Pressure sensors suitable for use include those available on the market which withstand high pressures that may be present within a sterilizer during a typical sterilization cycle or even slightly higher (e.g. up to 4 bar absolute). Also it is desirable to employ pressure sensors which have a low long term drift and that are calibrated and temperature compensated to ensure high accuracy.

(18) Temperature sensors used to measure the temperatures at the load(s) and/or in the sterilizer favorably have an accuracy of 1 K, more favorably of 0.5 K, even more favorably of 0.3 K, most favorably of 0.1 K. Temperature sensors used to measure the temperatures at the load(s) and/or in the sterilizer favorably have a high resolution, for example equal to or less than 0.1K, more favorably equal to or less than 0.02 K, and most favorably equal to or less than 0.01 K. Also it is desirable to employ temperature sensors which have a low long term drift and that are calibrated to ensure high accuracy.

(19) In the following, examples of calculations used to determine quantities non-condensable gas(es) versus the amount of steam based on the measured temperature of the load(s) and measured pressure and/or temperature in the sterilizer, the results of the calculations are in turn used to provide a measure of steam sterilant quality. Reference is made to the exemplary challenge device embodiment shown in FIG. 1, where the cylindrical tube has the height h.sub.Tube starting from the position adjacent to the lower edge of the thermal load up to the inner closed end of the bore. The innermost portion of the tube having a height h.sub.NCG is filled with non-condensable gas(es) and the outer part of the tube having a height h.sub.steam is filled with steam, not yet condensed. It is to be understood that NCGs collected at the innermost portion of the tube due to the continuous steam flow inwardly which in turn pushes NCGs inwardly. In the following, temperature in the sterilizer is referred to as steam temperature and as mentioned above this may be either measured directly using an appropriate temperature sensor or derived from pressure data measured using an appropriate pressure sensor.

(20) The total condensation energy of the steam condensed in the tube E.sub.steam can be calculated as follows:
E.sub.Steam(t)(T.sub.Load(t)T.sub.0).Math.C.sub.Load(I)

(21) with C.sub.Load=heat capacity of thermal load

(22) and T.sub.Load=temperature of thermal load

(23) and T.sub.0=temperature of thermal load at the beginning of the sterilization process

(24) The heating power of the steam P.sub.Steam in the tube can be calculated from the derivation of the energy E.sub.Steam with respect to time:

(25) $\begin{array}{cc}{P}_{\mathrm{Steam}}\left(t\right)=\frac{{\mathrm{dE}}_{\mathrm{Steam}}\left(t\right)}{\mathrm{dt}}=\frac{{\mathrm{dT}}_{\mathrm{Load}}\left(t\right)}{\mathrm{dt}}.Math.C_{\mathrm{Load}}& \left(\mathrm{II}\right)\end{array}$

(26) The heating power P.sub.Steam can also be calculated from the steam temperature T.sub.STEAM and the actual load temperature T.sub.Load assuming that the inner surface area of the tube has the temperature of the steam:

(27) $\begin{array}{cc}{P}_{\mathrm{Steam}}\left(t\right)=\frac{T_{\mathrm{Steam}}\left(t\right)-T_{\mathrm{Load}}\left(t\right)}{R}& \left(\mathrm{III}\right)\end{array}$

(28) with R=thermal resistance between the tube and the at least one thermal load With the abbreviation (t)=T.sub.Steam(t)T.sub.Load(t) equation (III) can be written as:

(29) $\begin{array}{cc}{P}_{\mathrm{Steam}}\left(t\right)=\frac{T\left(t\right)}{R}& \left(\mathrm{IV}\right)\end{array}$

(30) The thermal resistance R can be described as the quotient of the specific thermal resistance r of the tube and the contact area A between the load and the tube

(31) $\begin{array}{cc}R=\frac{r}{A}& \left(V\right)\end{array}$

(32) In case of a cylindrical tube which is in contact with the thermal load of the entire surface thereof as sketched in FIG. 1 the contact area A is a product of the height of the load h and the circumference of the tube U
A=h.Math.U(VI)

(33) In case non-condensable gas (NCG) is collected in the tube, it will insulate a part of the tube (or at least reduce heat transfer there from). Only that part of the tube that is filled with steam and is in thermal contact with the load will contribute to the heating power P.sub.Steam. This height is here called h.sub.Steam. Taking this into account with equation (IV, V, VI) one obtains:

(34) $\begin{array}{cc}{P}_{\mathrm{Steam}}\left(t\right)=\frac{T\left(t\right)}{r}.Math.h_{\mathrm{Steam}}.Math.U& \left(\mathrm{VII}\right)\end{array}$

(35) Equation (VII) can be transposed to h.sub.Steam resulting in:

(36) $\begin{array}{cc}{h}_{\mathrm{Steam}}\left(t\right)=\frac{P_{\mathrm{Steam}}\left(t\right).Math.r}{T\left(t\right).Math.U}& \left(\mathrm{VIII}\right)\end{array}$

(37) Using equation (II) yields:

(38) $\begin{array}{cc}{h}_{\mathrm{Steam}}\left(t\right)=\frac{\frac{{\mathrm{dT}}_{\mathrm{Load}}\left(t\right)}{\mathrm{dt}}.Math.C_{\mathrm{Load}}.Math.r}{T\left(t\right).Math.U}& \left(\mathrm{IX}\right)\end{array}$

(39) Equation (IX) generally shows that h.sub.Steam can be calculated from temperature measurements of the load and measured or derived temperature of the steam.

(40) The volume of NCG V.sub.NCG can be calculated from the inner volume of the tube V.sub.Tube (h.sub.Tube height of tube, r.sub.Tube inner radius of tube):
V.sub.Tube=h.sub.Tube.Math..Math.r.sub.Tube.sup.2(X)

(41) Assuming a clear separation of steam and NCG we get:
h.sub.Tube=h.sub.Steam+h.sub.NCG(XI)

(42) Transposing to h.sub.NCG yields:
h.sub.NCG=h.sub.Tubeh.sub.Steam(XII)

(43) Using equation (IX) e.g. we get height of NCG in the tube over time:

(44) $\begin{array}{cc}{h}_{\mathrm{NCG}}\left(t\right)=h_{\mathrm{Tube}}-\frac{\frac{{\mathrm{dT}}_{\mathrm{Load}}\left(t\right)}{\mathrm{dt}}.Math.C_{\mathrm{Load}}.Math.r}{T\left(t\right).Math.U}& \left(\mathrm{XIII}\right)\end{array}$

(45) Now the volume of non-condensable gas(es) V.sub.NCG can be calculated for example with following equation:
V.sub.NCG(t)=h.sub.NCG(t).Math..Math.r.sub.Tube.sup.2(XIV)

(46) To make the initially calculated volume of NCG V.sub.NCG independent of pressure and temperature, it is desirably to normalize the value.

(47) For example, using the ideal gas law
p.Math.V=n.Math.R.sub.m.Math.T(XV)

(48) the volume of NCG at a normal pressure and temperature, in particular at 101325 Pa and 23 C., V.sub.NCG.sub._.sub.normal can be calculated

(49) $\begin{array}{cc}{V}_{\mathrm{NCG}\_\mathrm{normal}}=V_{\mathrm{NCG}\_\mathrm{in}\_\mathrm{ETS}}.Math.\frac{p_{\mathrm{NCG}\left(=\mathrm{Chamber}\right)}}{p_{\mathrm{normal}}}.Math.\frac{T_{\mathrm{normal}}}{T_{\mathrm{NCG}\left(=\mathrm{Chamber}/\mathrm{Tube}\right)}}& \left(\mathrm{XVI}\right)\end{array}$

(50) From the volume one can also derive the mass of NCG m.sub.NCG, for example using the following formula:

(51) 0$\begin{array}{cc}{m}_{\mathrm{NCG}}=\frac{V_{\mathrm{NCG}\_\mathrm{normal}}}{24.3l\text{/}\mathrm{mol}}.Math.m_{\mathrm{mol}}& \left(\mathrm{XVIb}\right)\end{array}$

(52) where m.sub.mol is 29 g/mol and 24.3 l/mol represents the volume of 1 mol of gas under normal conditions, i.e. at 101.325 kPa and 23 C.

(53) The mass of steam, which is condensed in the tube can be obtained by using the equation:
E.sub.Steam=H.sub.Steam.Math.m.sub.Steam(XVII)

(54) with

(55) $H_{\mathrm{Steam}}39\frac{\mathrm{kJ}}{\mathrm{mol}}=\mathrm{specific}\mathrm{condensation}\mathrm{heat}$
m.sub.Stream=mass of steam in mol

(56) and equation (I):
E.sub.Steam(t)=(T.sub.Load(t)T.sub.0).Math.C.sub.LoadH.sub.Steam.Math.m.sub.Steam(XVIII)

(57) Transposing results in:

(58) $\begin{array}{cc}{m}_{\mathrm{Steam}}\left(t\right)=\frac{\left(T_{\mathrm{Load}}\left(t\right)-T_0\right).Math.C_{\mathrm{Load}}}{H_{\mathrm{Steam}}}& \left(\mathrm{XIX}\right)\end{array}$

(59) For higher accuracy instead of using a constant value of H.sub.steam independent of the temperature, a value for H.sub.Steam may be determined on the basis of measured temperature (or, if applicable, determined via measured pressure), yielding

(60) $\begin{array}{cc}{m}_{\mathrm{Steam}}\left(t\right)=\frac{\left(T_{\mathrm{Load}}\left(t\right)-T_0\right).Math.C_{\mathrm{Load}}}{H_{\mathrm{Steam}}\left(T_{\mathrm{Steam}}\right)}& \left(\mathrm{XIXb}\right)\end{array}$

(61) If desired, the quantity of condensed steam can be given in terms of volume (V.sub.steam) where the V.sub.steam is equal to the m.sub.steam divided by the density of water.

(62) As can be recognized from above, the quantities of NCG and steam collected in the tube during a selected time interval t may be calculated in terms of either volume or mass, by using challenge devices as described herein, measured temperature measurements of the thermal load(s) and measured pressure and/or temperature in the sterilizer. Any appropriate ratio of these determined quantities of NCG and steam (e.g. V.sub.NCG/m.sub.steam, V.sub.NCG/V.sub.steam, m.sub.NCG/m.sub.steam and m.sub.NCG/V.sub.steam) may serve as a good measure for steam quality. However it is desirable to use ratio V.sub.NCG/m.sub.steam or V.sub.NCG/V.sub.steam since the determination of mass of NCGs required additional calculations while mass and volume of steam are essentially the same value since the density of water is one. Making reference to section 13.3.2 DIN EN 285, a value of greater than 3.5% V/V would seem to be an indicator of poor quality (as well as an indicator of some potential issue(s) with either the steam generator or sterilizer). Clearly a value approaching 0% would be ideal in terms of efficacy of sterilization. To allow for a desirable indicator of efficacy of sterilization, correlation studies may be made with side-by-side quality of steam determinations as described herein together with microbicidal efficiency determinations so that a particular value steam quality determined during sterilization may be correlated to a particular level of residual microbial activity after sterilization.

(63) The aforesaid example refers to a case where a single load is used, where its temperature as well as the temperature of steam are used in the equations. Again temperature in sterilizer may be directly measured or derived from measured pressure in the sterilizer. Although not shown in the equations, as mentioned above the skilled person knows how to derive temperature from pressure data, and the skilled person will know how to use measured pressure data and appropriately incorporate such data into the calculations illustrated by the equations shown above. The aforesaid calculations were made using data of and from a challenge device having a tube with a bore having a constant diameter along its length. However, it will be recognized by the skilled person that the equations and calculations shown above may be appropriately adjusted in case of other geometries, e.g. a conical-like tube bore.

(64) Methods in accordance may be applied to cases where challenge devices having two or more than one thermal loads are used.

(65) FIG. 2 shows a sketch of an exemplary challenge device including more than one thermal load. As in the first exemplary embodiment the device include a tube (1) but now three loads (3a), (3b) and (3c) located around the tube. Again there is a foil (4) between the tube and the loads. Favorably, the temperature of each thermal load is measured by means of a temperature sensor (5a, 5b, 5c) associated with an individual load. Similar to the exemplary challenge device shown in FIG. 1, the exemplary challenge device of FIG. 2 favorably includes a temperature sensor (6) as well as a pressure sensor (7) which allow for the measurement of temperature and pressure, respectively, inside the sterilizer (i.e. measurement of unchallenged temperature and pressure).

(66) In such a case the amount of non-condensable gas(es) can be calculated in the same way as shown above. It just has to be done for every load, i.e. the determination of the height of the step according to equation (IX) is solved for each and every load. In case, the load is adjacent to a portion of the tube where there is only NCG (as is the case for load (3a) in FIG. 2), h.sub.Steam will be equal to zero. In case the load is adjacent to a portion of the tube where there is only steam (as is the case for load (3c) in FIG. 2), h.sub.Steam will be equal to the height of the load. In case the load is adjacent to a portion of the tube where there is both NCG and steam (as is the case for load (3b) in FIG. 2) the value of h.sub.Steam will be between zero and the height of the load in proportion to the amounts of NCG and steam (in FIG. 2 the amount of NCG and steam is 1 to 1 and thus the h.sub.Steam is one half the height of the load).

(67) Now h.sub.Steam for every load which is covered at least in part with steam has to be summed up, resulting in h.sub.Steam, total for the whole tube (s. equation (XX)), considering the spacing between the loads (which would preferably be between about 1 mm and about 4 mm).

(68) $\begin{array}{cc}{h}_{\mathrm{Steam},\mathrm{total}}\left(t\right)=\underset{i}{.Math.}\left(h_{\mathrm{Steam},i}\left(t\right)+h_{\mathrm{Spacing},i}\right)& \left(\mathrm{XX}\right)\end{array}$

(69) This value can then be used for the further calculations in analogy to the calculations shown above.

(70) The calculation of the total amount of condensed steam is similar to equation (XIX). The amount of condensed steam of every load may be summed up as shown in the following equation:

(71) $\begin{array}{cc}{m}_{\mathrm{Steam}}\left(t\right)=\underset{i}{.Math.}\frac{\left(T_{\mathrm{Load},i}\left(t\right)-T_{0,i}\right).Math.C_{\mathrm{Load},i}}{H_{\mathrm{Steam}}}& \left(\mathrm{XIXB}\right)\end{array}$

(72) Evidently, other modifications to the above algorithm may be made without departing from the scope of the present disclosure.

(73) FIG. 3 shows curves of measured parameter for a typical sterilization run using an exemplary challenge device having two thermal loads with a temperature sensor at each load as well temperature and pressure sensor for measuring the temperature and pressure in the sterilizer. The graph shows the measured temperature inside the sterilizer (but outside of the tube bore) over time (curve 20); the measured pressure (curve 21) inside the sterilizer over time as well as the measured temperature at lower, outer thermal load (curve 22) and the inner, upper thermal load (curve 23) over time. The sterilization run includes three purges, i.e. evacuation and (partially) filling with steam, and after the last evacuation, the sterilization phase is started where the sterilizer is pumped with steam sterilant so that the temperature within the sterilizer reaches 134 C.

(74) FIG. 4 shows the same measured temperature data shown in FIG. 3 (curves 20, 22, 23) together some calculated parameters. One of these is the mass of condensate, i.e. condensed steam, during the cycle over time (curve 24). Another two of these include the height of NCG-level in the tube over time (curve 25) and volume of NCG over time normalized to 101.325 kPa and 23 C. (curve 26). The latter curve is very low relative to the former due to inter alia the normalization. It will be appreciated that during the purging phase the amount of NCGs in the sterilizer and correspondingly in the bore of the tube falls dramatically, and as shown in FIG. 4 during the sterilization phase the amount of NCGs in the tube slowly climbs as ever increasing amounts of NCGs are collected within the tube over time. Ideally when there were no NCGs in the steam sterilant and the sterilizer is perfectly sealed and all NCGs were removed during purging phase, the amount of NCGs found in the sterilizer during a sterilization phase would be or would approach zero. The curve labeled curve 27 in FIG. 4 is the calculated steam quality (NCG concentration) derived from the volume of the NCG at ambient/standard conditions and the volume of condensate. It should be appreciated that the illustrated experiment in FIG. 4 represents a non-ideal run where the NCG concentration is unfavorably high. High NCG concentrations can be the result of a number of factors including e.g. leakage along the steam-inlet pipe installation and/or adaptors of the sterilization chamber.

(75) FIGS. 5 and 6 show schematic sketches of configurations of systems in accordance with the disclosure in relation to a steam sterilizer (10). In one configuration as shown in FIG. 5, a system may be composed of two appliances, one appliance (11) including the challenge device (13) and data collection unit (14) to be inserted into the chamber of a steam sterilizer and the second appliance (12) including a data evaluation unit (15). Data evaluation units generally include a visual display. They may be computers. Alternatively they may be handheld computing devices or any other suitable computing devices. Typically data is transferred automatically from the data collection unit to data evaluation unit either through wires or wireless. Evaluation units may be mounted onto an outer surface of the sterilizer or be detached from the sterilizer (as shown in FIG. 5). In an alternative configuration, such as that shown in FIG. 6, a system may be a single appliance (16) including the challenge device (13), data collection unit (14) as well as the data evaluation unit (15). Such an appliance favorably includes a visual display.

(76) Methods and systems described herein provides several advantages over the prior art. For example, methods and systems described herein can effectively make use of challenge devices requiring only a single or a low number of loads (e.g. two or three). This allows for a simplification of the challenge device, which accordingly at the same time, provides for the use of less sensors. In fact, in the most simple embodiments where the challenge device has one load, the device may only comprise two temperature sensors or a single temperature and a single pressure sensor. This is advantageous in that a low number of interfering heat bridges are generated and the resulting data analysis is much easier. Thus, methods and systems described herein allow for the use of challenge devices that are less expensive, easier to build, require less electronics and may be significant smaller in size. Finally, a quantitative assessment of the steam quality may be achieved using a comparably simple device.