WO2015109308A1

WO2015109308A1 - Rotary valve

Info

Publication number: WO2015109308A1
Application number: PCT/US2015/012020
Authority: WO
Inventors: George E. Anderson; Benjamin W. Floan
Original assignee: Crown Iron Works Company
Priority date: 2014-01-17
Filing date: 2015-01-20
Publication date: 2015-07-23

Abstract

A thermally conditionable rotary valve is provided. The valve is generally characterized by a valve housing and a valve rotor. The valve housing is configured to operatively retain the valve rotor. Material is passable from a valve housing ingress to a valve housing egress via operation of (i.e., passage by/through) the valve rotor. The valve housing Is adapted for select thermal conditioning in furtherance of establishing a user select temperature T1 for the valve housing. The valve rotor is rotatable within the valve housing in furtherance of passing material from the housing ingress to the housing egress.

Description

ROTARY VALVE

This is an international application filed under 35 USC §363 claiming priority under 35 USC §120 of/to U.S. Pat. Appl . Ser. No. 61/928, 837 filed January 17, 2014 and entitled ROTARY VALVE, the 5 disclosure of which is hereby incorporated by reference in its entirety .

TECHNICAL FIELD

The present invention deals with the field of material or L0 product transfer, more particularly, to an assembly directed to material/product transfer between areas of differing pressure while maintaining the pressure differential and material/product flow. The assembly functions to manage (e.g., prevent) material/product loss in a space between a wall of a housing through which a rotor L5 associated therewith passes. The space, though unintended, typically but not exclusively is created because of different measures of expansion of the housing and the rotor during operation .

BACKGROUND OF THE INVENTION

Rotary valves are devices that regulate, direct or control the flow of a material, e.g., a fluid (i.e., gases, liquids, fluidized solids, or slurries) by opening, closing, or partially obstructing various passageways. More particularly, it is a type of valve in which the rotation of a passage or passages in a transverse plug regulates fluid flow therethrough. Passage of material, commonly but not exclusively, powdered or granule solids, is enabled between areas of differing pressure while nonetheless maintaining the pressure differential and the material flow. Airlocks, which are functionally equivalent to rotary valves, are devices which permit the passage of material between a pressure vessel and its surroundings while minimizing the change of pressure in the vessel and loss of air from it.

Rotary valves are characterized by a valve housing and a valve rotor. The valve housing is generally configured to operatively retain the valve rotor which is rotatable therein in furtherance of passing material from a housing ingress/ingress conduit to a housing egress/egress conduit. The valve rotor in turn is characterized by a plurality of radially extending vanes or blades, which in combination with the valve housing, delimit pockets or compartments, each characteristic of either of the valve ingress or valve egress product or materials as a function of valve rotor rotation position.

The valve rotor may be directly or indirectly driven for rotation, and may be of a variety of types, e.g., sanitary, reduced capacity, multi-vane, helical, disc-end, etc., form generally fitting function or application. Moreover, configurations of/for the valve include "blow through" (CV) wherein product/material discharges horizontally at a 90 degree angle relative to the inlet via a pneumatic (pressure or vacuum) conveying line, or "drop through" (DT) wherein product/material discharges vertically downwards from the bottom outlet.

The relationship for, among and between the rotor housing and the rotor valve, more particularly, the rotor vanes and the house is not trivial. While almost exclusively manufactured to a select tolerance, in service conditions commonly alter the tolerance between the vane tips and the rotor housing, as do operator alterations in furtherance of specific operational aims. This is particularly evident in the context of vacuum service and/or processes characterized by temperature swings during start-up and/or operation, common but hardly exclusive scenarios wherein rotary valve leakage can be and often times is significant. While close tip tolerances are needed to prevent or stop valve leakage, uneven heating very often results in plant operators grinding the vanes so as to overcome interference between valve components at start-up .

By way of illustration, in an application characterized by a 20 psi differential (e.g., 22 psig density steam exchanged for 2 psig density steam) , two vanes usually blocking leaks, and a 44 inch diameter, 20 inch long rotor, the valve will "pump" about 158#/hr of steam @~235°F and 5rpm (vessel leakage) because of the rotation of the rotor and its displacement. Critically, it will "leak" about 2,000#/hr of steam through a gap at the rotor tips and sides, with a relatively "tight" gap estimated at about 0.015 inch (i.e., a valve clearance, relative to the housing, of a nominal 0.030 inch diameter) . A tight gap means careful machining, however, a common problem is that the rotor and housing typically expand during start-up, operation and shut-down, and seldom do they reach the same/similar temperature at the same time.

Typically, the rotor expands more quickly than does the housing. This results in binding of the rotor within the housing and consequent squealing. In cases where the housing expands more quickly than does the rotor, the gap will result, and, in certain circumstances, the gap can be as much as four times the cross section as it would normally be. In either case discussed above, it might be necessary to grind one or both of the components to enable optimum operation. Frequently, however, such attempts result in even more leakage and the commensurate costs for wasted steam.

It is to these problems and shortcomings in the prior art that the present invention is directed. It enables efficient operation of the vessel and protects against both large leakage gaps and binding of the rotor valve within the rotor housing.

SUMMARY OF THE INVENTION

The present invention contemplates an apparatus and method for thermal conditioning of a housing and a rotor mounted therewithin. Both the housing and rotor are selectively submitted to heating so as to enable selective control of the sizing of an inner circumferential surface of the housing and the outer circumferential surface of the rotor mounted within the housing. Heated fluid is channeled to the desired surface (s) of the vessel to facilitate easy and efficient operation of the vessel. The heated fluid is directed to a manifold or any other appropriate structure designed to accomplish engagement of the fluid with the appropriate surface.

In an advantageous, non-limiting embodiment, a thermally conditionable rotary valve is provided. The valve is generally characterized by a valve housing and a valve rotor. The valve housing is configured to operatively retain the valve rotor. Material is passable from a valve housing ingress to a valve housing egress via operation of (i.e., passage by/through) the valve rotor. The valve housing is adapted for select thermal conditioning in furtherance of establishing a user select temperature Tl for the valve housing. The valve rotor is rotatable within the valve housing in furtherance of passing material from the housing ingress to the housing egress. The valve rotor includes a plurality of spaced apart vanes, a hub from which vanes of the plurality of spaced apart vanes radially extend, and a shaft upon which the hub is operatively supported. The valve rotor is adapted for select thermal conditioning in furtherance of establishing a user select temperature T2 for the valve rotor. Contemplated thermal conditioning includes scenarios wherein T1~=T2, TKT2, and T1>T2. More specific features and advantages obtained in view of those features will become apparent with reference to the drawing figures and DETAILED DESCRIPTION OF THE INVENTION.

BRIEF DESCRIPTION OF THE DRAWINGS

The assembly, subassemblies, apparatus, structures and/or elements disclosed directly or implicitly herein may be embodied in other specific forms without departing from the spirit or general characteristics thereof, some of which forms have been indicated. Thus, the features described and depicted herein/herewith are to be considered in all respects illustrative and not restrictive. Moreover, in-as-much-as structures have been assigned select unique reference characters through the subsequent written description, and which correlate to at least one drawing of the instant drawings, the identification of all depicted structures in any given drawing via the inclusion of reference characters has been superceded for the sake of clarity. The drawings are described as follows:

FIG. 1 depicts, perspective end view, slightly from above, a rotary valve or airlock;

FIG. 2 depicts a side view of the rotary valve of FIG. 1; FIG. 3 depicts an alternate, opposite side view of the rotary valve of FIG. 1, hidden features generally indicated;

FIG. 4 depicts an end view of the rotary valve of FIG. 1, hidden features generally indicated;

FIG. 5 depicts section 5-5 of the rotary valve of FIG. 2, namely, a lateral midline cross-section thereof;

FIG. 6 illustrates particulars of area 6 of FIG. 5, namely, details of a relationship between a free end of a rotor vane and a rotor housing;

FIG. 7 depicts section 7-7 of the rotary valve of FIG. 3, namely, particulars regarding rotor elements in relation to rotor casing elements, more particularly, those in connection to the rotor and an end wall of the housing thereof;

FIG. 8 depicts section 8-8 of the rotary valve of FIG. 3, namely, a longitudinal midline cross-section of an end wall of a rotor casing thereof;

FIG. 9 depicts section 9-9 of the rotary valve of FIG. 4, namely, a longitudinal midline cross-section thereof;

FIG. 10 depicts, perspective end view, slightly from above, the rotor housing of the rotary valve of FIG. 1;

FIG. 11 depicts, perspective side view, slightly from above, the rotor of the rotary valve of FIG. 1;

FIG. 12 depicts a side view of the rotary valve housing of FIG. 1, hidden features generally indicated;

FIG. 13 depicts a end view of the rotary valve housing of FIG. 1, hidden features generally indicated;

FIG. 14 depicts a side view of the rotary valve of FIG. 11, hidden features generally indicated; and,

FIG. 15 depicts a end view of the rotary valve of FIG. 11, hidden features generally indicated.

DETAILED DESCRIPTION OF THE INVENTION

A thermally conditionable rotary valve or airlock is notionally provided. More particularly, the instant rotary valve is characterized by separate and independent thermally conditionable components, namely, a thermally conditionable valve housing and a thermally conditionable valve rotor. For the sake of non-limiting illustrative context, an advantageous embodiment of the instant rotary valve is generally depicted in FIG. 1. A variety of assembly views are provided for in FIGS. 2-4, with selection sectional views and/or particulars for the assembly and/or structures thereof provided for in FIGS. 5-9. Assembly components are likewise depicted, more particularly, the representative non-limiting valve housing of the FIG. 1 assembly is illustrated in the several views of each of FIGS. 10, 12 & 13, with the representative non-limiting rotor valve of the FIG. 1 assembly illustrated in the several views of each of FIGS. 11, 14 & 15. Finally, as to the drawing sheets, six (6) are sequentially presented, more particularly, sheet 1/6 includes a single figure showing the instant rotary valve; sheet 2/6 includes three figures (2, 5 & 6) showing a side valve view, a lateral valve bisection, and related details regarding the latter; sheet 3/6 includes three figures (3, 7 & 8) showing a further, opposing side valve view with internal elements indicated in broken 5 lines, and two select sections thereof; sheet 4/6 includes two figures (4 & 9) showing an end elevation with internal elements indicated in broken lines, and a longitudinal bisection; sheet 5/6 includes three figures (10, 12 & 13) showing several views of the valve housing of FIG. 1; and, sheet 6/6 includes three figures (11,

L0 14 & 15) showing several views of the valve rotor of FIG. 1. Prior to a discussion of the drawing particulars, preliminary observations are warranted.

Notionally, thermal conditioning, more particularly, relative thermal conditioning of rotary valve components is sought. While

L5 convection (i.e., heat transfer using a fluid) is contemplated, believed advantageous, and generally supported by the depicted rotary valve, it need not be so limited. Alternate thermal conditioning may be effectuated via rotary valve adaptations conducive to alternate means of heat transfer, namely conduction

20 (i.e., heat transfer through solids), or radiation (i.e., heat transfer using electromagnetic energy) . As to convection, while water, oil or glycols are contemplated, other fluids having advantageous and/or desirable thermal transfer properties are considered to be well known to those of ordinary skill in the art. Moreover, while "gap" management is an objective of the contemplated thermal conditioning, it need not be the exclusive objective of the contemplated thermal conditioning. For instance, and without limitation, select thermal conditioning during processing may prove advantageous in relation to the quality and/or character of the product or material being processed, and/or to impart a change in its quality and/or character while passing from the valve housing ingress to the valve housing egress.

Referring now initially and generally to FIGS. 1-4, & 10-15 there is shown a rotary valve 20 in several views (FIGS. 1-4) having thermally conditionable components, namely, a valve housing 30 (see also the several housing views of FIGS. 10, 12 & 13) adapted for select thermal conditioning in furtherance of establishing a user select temperature Tl for the housing, and a valve rotor 100 (see also the several rotor views of FIGS. 11, 14 & 15) adapted for select thermal conditioning in furtherance of establishing a user select temperature T2 for the valve rotor. Thermal conditioning of the housing is independent and advantageously, but not necessarily, separate from thermal conditioning of the valve. Moreover, and as will be later detailed, each of the housing and valve adaptations advantageously, but not exclusively, are characterized by fluid flow/passage channels and/or compartments. Generally, a thermal conditioning/conductive fluid is passed to and through the valve housing, as by a double wall adaptation thereof, and a conductive fluid is likewise passed to and through a valve, as by a fluid passage therethrough, or fluidly linked passages of most, if not all primary valve elements. Moreover, the either of the housing and/or the valve may include baffles or the like to selectively direct the thermal conditioning fluid, with it believed advantageous to provide same in connection to a vane adaptation, e.g., a baffled vane cavity.

In advance of a focus upon the subject thermally conditionable rotary valve per se, i.e., the valve assembly and the relationship for, between and among its contemplated constituent elements viz-a- viz the particulars of sheets 2/6-4/6 (e.g., FIGS. 5-9), some overview or contextual description follows. More particularly, a valve overview is initially provided with reference to FIG. 1, and selectively to any of the valve housing figures of sheet 5/6 and/or the valve rotor figures of sheet 6/6. Thereafter, assembly particulars of sheets 2/6-4/6 (i.e., FIGS. 2, 5 & 6; FIGS. 3, 7 & 8; and, FIGS. 4 & 9) are presented.

With particular reference to FIG. 1, and select reference to FIGS. 10, 12 & 13 on one hand, and FIGS. 11, 14 & 15 on the other hand, thermally conditionable rotary valve 20 includes valve housing 30 (FIGS. 10, 12 & 13) configured to operatively retain valve rotor 100 (FIGS. 11, 14 & 15), material passable from a valve housing ingress or inlet 32, characterized by pressure PI, to a valve housing egress or outlet 34, characterized by pressure P2, via operation of (i.e., passage by/through) valve rotor 100. The valve housing may be fairly characterized as having opposing longitudinal walls or wall portions (i.e., arcuate sidewalls 36; e.g., FIG. 13) and opposing lateral walls or wall portions (i.e., 5 planar end walls 38; see e.g., FIG. 12) which, in combination, delimit a cavity 40 (e.g. FIG. 13) within which valve rotor 100 substantially resides.

Valve rotor 100, rotatable within valve housing 30 in furtherance of passing material from housing ingress 32 to housing

L0 egress 34 (see also, e.g., FIG. 13), generally includes a plurality of spaced apart vanes or blades 102 (see also, e.g., FIG. 15), a hub 104 (see e.g., FIG. 15) from which vanes 102 of the plurality of spaced apart vanes radially extend, and a shaft 106 (see also, e.g., FIGS 11 & 14) upon which hub 104 is operatively supported or

L5 united. In the depicted rotary valve, the vanes longitudinally extend between end-discs 108 (see also, e.g., FIG. 11) . In connection to the instant depiction, housing ingress 32 and egress 34 are delimited by apertured flanges 42 (see also, e.g., FIG. 13) such that the rotary valve may operatively link areas of differing

20 pressures (i.e., PI & P2) as by an ingress/egress conduit or the like (e.g., a duct, pipe, etc., not shown) . Notionally, shaft 106 of valve rotor 100, via its keyed end 110, is rotated such that each pocket of pockets 112 of the valve (see e.g., FIG. 15), delimited by adjacent vanes 102 of valve rotor 100, travel 180 degrees between the inlet/outlet conduit and the outlet/inlet conduit (i.e., pressures P1/P2, and P2/P1) in furtherance of transferring material through the valve housing while generally maintaining the pressure differential (e.g., P2>P1) between the conduits .

The valve housing generally and advantageously includes one or more compartments, conduits, passages, etc. for receipt and passage of a thermal conditioning fluid in furtherance of select thermal conditioning of the valve housing. As is best appreciated with reference to FIGS. 12 & 13, housing 30 is advantageously, but not exclusively, characterized by a double wall construction. Bilateral arcuate sidewalls 36 include a cavity 44 delimited by inner 46 and outer 48 sidewall portions. The outer sidewall portions 48 include ports 50 for fluid ingress and egress with regard to sidewall cavity 44. Consistent with its two part configuration, discrete cavities are contemplated and correspond to the discrete sidewalls of the valve housing. Further division (s) of the illustrated bilateral cavities are believed advantageous but not essential.

The valve rotor generally and advantageously includes one or more compartments, and as to the latter, advantageously but not necessarily in fluid communication, for receipt and passage of a thermal conditioning fluid in furtherance of select thermal conditioning of the valve housing. As is best appreciated with reference to FIG. 14, shaft 106 of valve rotor 100 is adapted to include a longitudinally extending passage 114 for receipt and passage of a thermal conditioning fluid. Notionally, the thermal conditioning fluid enters a first shaft end and passes therethrough for egress at a second shaft end. Moreover, and advantageously, 5 further valve rotor structure adaptations are contemplated in furtherance of enhanced heat transfer. For instance, and as is best appreciated with reference to FIGS. 14 & 15, vanes 102 of valve rotor 100 are adapted so as to include a cavity or void 116. Advantageously, but not exclusively, cavities 116 appreciably

L0 extend in both the lateral (radial; see FIG. 15) and longitudinal

(see FIG. 14) directions of vanes 102. Moreover, opposing surfaces of end discs 108 of valve rotor 100 are adapted, as by machining or the like, so as to include a relief area or channel 118 which circumscribes shaft 106 passing therethrough, with shaft portions

L5 also adapted, as by drilling or the like, so as to include one or more radially extending passages 120 which link longitudinal extending shaft passage 114 to vane cavities 116 via end disc relief areas 118. Via such exemplary configuration, thermal conditioning fluid enters a first shaft end and passes both

20 directly therethrough, for egress at the second shaft end, and radially into a first disc end and thereafter to and through the vane cavities, into and through the relief area of the second disc end for joinder to/with the longitudinally extending shaft passage via the radial passages. During steady state operation, the shaft, portions of the disc ends and the vanes of the valve rotor pass thermal conditioning fluid in furtherance of thermal conditioning of the valve rotor.

With renewed reference now to the assembly of FIG. 1, a 5 variety of views, sections and details are shown with reference to sheets 2/6-4/6. With reference to sheet 2/6, a side view of the rotary valve of FIG. 1 is generally illustrated in FIG. 2. A lateral bisection thereof, illustrating adaptations of/for both housing 30 and valve rotor vanes 102, is provided (FIG. 5) . Select

L0 relationships with regard to the valve rotor are indicated, e.g., vane 102/hub 104 particulars, details of/for a double walled housing with fluid ingress/egress ports 50 are also provided, and finally, the nature of the gap for between and among the housing (i.e., an inside surface of inner wall 46 of the double walled

L5 housing as shown) and vane tip or free end 103 is shown, with details thereof in FIG. 6. Notionally, it is this gap that is "managed" via the thermal conditioning of the instant thermally conditionable rotary valve. For example, and without limitation, during "cold" start up, the housing may be heated preferentially to

20 avoid binding (i.e., a "zero" gap condition) . Subsequent to the establishment of product/material flow, the rotor may be selectively heated to establish and maintain controlled tight clearance for minimal leakage via the gap. As a practical matter, a 24 inch diameter stainless rotor will expand approximately 0.029 inches owing to a temperature rise of 70 to 200°F; the difference in expansion with a steel housing and a stainless rotor is 0.009 inches and clearance will tighten if parts heat evenly; the difference in expansion with a stainless housing and a steel rotor is 0.009 inches and clearance will loosen if parts heat, resulting is increased/increasing leakage. Finally, it is to be appreciated that thermal conditioning includes advantage beyond gap management, e.g., to manage, control, avoid, etc. condensation, freezing, etc.

With reference now to sheet 3/6, a further side view of the rotary valve of FIG. 1, hidden features generally indicated, is generally illustrated in FIG. 3. In combination, FIG. 3 and the sectional views of FIGS. 7 & 8 illustrate a representative, non- limiting robust manifold for the passage of thermal conditioning fluid to and through a substantial portion of the valve rotor. For example, relationships for, between and among vane cavities 116, end disc relief areas 118, radial shaft passages 120 and longitudinally extending shaft passage 114 of valve rotor 100 (FIGS. 11, 14 & 15), in connection to valve housing 30, are generally illustrated, and particularly illustrated in the longitudinal midline cross-section of end wall 38 of rotor casing 30 as per FIG. 8.

Finally, with reference now to sheet 4/6, an end view of the rotary valve of FIG. 1, hidden features generally indicated, is generally illustrated in FIG. 4. In combination, FIG. 4 and the sectional view of FIG. 9 further illustrate the representative, non-limiting robust manifold for the passage of thermal conditioning fluid to and through a substantial portion of the valve rotor. For example, relationships for, between and among vane 5 cavities 116, end disc relief areas 118, radial shaft passages 120 and longitudinally extending shaft passage 114 of valve rotor 100 (FIGS. 11, 14 & 15), in connection to valve housing 30, are generally illustrated, and particularly illustrated in the longitudinal bisection of the FIG. 1 rotary valve as per FIG. 9.

L0 Since the structures of the assemblies, subassemblies, and/or mechanisms disclosed herein may be embodied in other specific forms without departing from the spirit or general characteristics thereof, some of which forms have been indicated, the embodiments described and depicted herein/with are to be considered in all

L5 respects illustrative and not restrictive. Moreover, while nominal processing has been described and detailed, and to some degree alternate work pieces and systems, assemblies, etc. with regard thereto referenced, contemplated processes are not so limited. Accordingly, the scope of the subject invention is as defined in

20 the language of the appended claims, and includes not insubstantial equivalents thereto.

Claims

What is claimed is:

1. A thermally conditionable rotary valve comprising:

a. a valve housing configured to operatively retain a valve rotor, material passable from a valve housing ingress to a

5 valve housing egress via operation of the valve rotor, said valve housing adapted for select thermal conditioning in furtherance of establishing a user select temperature Tl for said valve housing; and,

b. a valve rotor, rotatable within said valve housing in LO furtherance of passing material from said housing ingress to said housing egress, said valve rotor including a plurality of spaced apart vanes, a hub from which vanes of said plurality of spaced apart vanes radially extend, and a shaft upon which said hub is operatively supported, said valve rotor adapted L5 for select thermal conditioning in furtherance of establishing a user select temperature T2 for said valve rotor.

2. The rotary valve of claim 1 wherein said select thermal conditioning in furtherance of establishing a user select

20 temperature Tl comprises heat transfer via convection.

3. The rotary valve of claim 1 wherein said select thermal conditioning in furtherance of establishing a user select temperature T2 comprises heat transfer via convection.

4. The rotary valve of claim 1 wherein said select thermal conditioning in furtherance of establishing a user select temperature Tl and T2 comprises heat transfer via convection.

5 5. The rotary valve of claim 1 wherein said select thermal conditioning in furtherance of establishing a user select temperature Tl and T2 comprises heat transfer selected from the group consisting of convection and conduction.

LO 6. The rotary valve of claim 1 wherein said select thermal conditioning in furtherance of establishing a user select temperature Tl and T2 comprises identical heat transfer mechanisms.

7. The rotary valve of claim 1 wherein said select thermal L5 conditioning in furtherance of establishing a user select temperature Tl and T2 comprises differing heat transfer mechanisms.

8. The rotary valve of claim 1 wherein an established user select temperature Tl is substantially equal to an established user select

20 temperature T2.

9. The rotary valve of claim 1 wherein an established user select temperature Tl is greater than an established user select temperature T2.

10. The rotary valve of claim 1 wherein an established user select temperature Tl is less than an established user select temperature T2.

5 11. The rotary valve of claim 1 wherein an established user select temperature Tl comprises a temperature profile corresponding to one or more of start-up operations, steady state material flow operations, and/or shut down operations.

L0 12. The rotary valve of claim 1 wherein an established user select temperature T2 comprises a temperature profile corresponding to one or more of start-up operations, steady state material flow operations, and/or shut down operations.

L5 13. The rotary valve of claim 1 wherein an established user select temperature Tl comprises a temperature profile corresponding to one or more of start-up operations, steady state material flow operations, and/or shut down operations, and temperature T2 likewise comprises a temperature profile corresponding to one or

20 more of start-up operations, steady state material flow operations, and/or shut down operations.

14. The rotary valve of claim 1 wherein said valve housing comprises one or more compartments for receipt and passage of a thermal conditioning fluid in furtherance of select thermal conditioning of said valve housing.

15. The rotary valve of claim 1 wherein said valve housing comprises one or more discrete compartments for receipt and passage of a thermal conditioning fluid in furtherance of select thermal conditioning of said valve housing.

16. The rotary valve of claim 1 wherein said valve housing comprises a double walled housing for receipt and passage of a thermal conditioning fluid in furtherance of select thermal conditioning of said valve housing.

17. The rotary valve of claim 1 wherein said shaft of said valve rotor is adapted for select thermal conditioning in furtherance of establishing a user select temperature T2 for said valve rotor.

18. The rotary valve of claim 1 wherein said shaft and vanes of said plurality of vanes of said valve rotor are adapted for select thermal conditioning in furtherance of establishing a user select temperature T2 for said valve rotor.

19. The rotary valve of claim 1 wherein said shaft of said valve rotor includes a longitudinally extending passage for receipt and passage of a thermal conditioning fluid, and vanes of said plurality of vanes of said valve rotor including a cavity for receipt and passage of the thermal conditioning fluid, said cavities and said longitudinally extending passage in fluid communication in furtherance of establishing a user select temperature T2 for said valve rotor.