Advanced roped hydraulic elevator with and without counterweight for all heights and speeds.

Field of the invention:

This invention relates to inventive counterweighted and counterweighfless roped hydraulic elevators that will apply 7: 1 or 9: 1 roping arrangements and a gearless and geared hydro-traction sheave that will be able to reach all heights with all speeds.

Background Art:-

Hydraulic elevators are commonly used for low rise applications but they have so many drawbacks which I will eliminate through my inventive embodiments: -

1 - Hydraulic elevators are commonly used just for low rise applications (up to 8- 10 floors )

2- Hydraulic elevators operate at low speed (typically 100 to 150 - 200 foot per minute)

3- In order for the elevator car to be able to reach higher floors longer cylinder must be used and this is very expensive.

4- Hydraulic elevators use much energy than traction elevators.

5- Safeties in hydraulic elevators are less than traction elevators.

To overcome the short travel height of the hydraulic elevators, 2: 1 roping is used in hydraulic elevators which enables the car to travel twice the stroke of the piston but this was not sufficient to make hydraulic elevators reach higher floors.

EP 0687644 Bl discloses the possibility of using 3:1 or 4:1 roping arrangement which enables the hydraulic elevator reach higher heights with short cylinder. However, this roping arrangement is still disadvantageous for it can not reach more higher floors and it is not counterweighted; thus this arrangement will use much energy than traction elevators. In previous art, traction elevators without counterweight are used to save space of the shaft that is very precious for the building or for making larger elevator cars.

To prevent the ropes from slipping on the traction sheave, springs and hydraulic cylinders were used in prior art passively for keeping tension and this tension is calculated according to the maximum load for safety considerations. Consequently, faster wearing in the hoisting ropes and in the rope groves of the rope pulleys ensues from the use of the maximum tension although elevators are rarely driven with maximum load.

To achieve the proper tension of the hoisting ropes for all loading situations, a solution was presented in the patent number US 7,798,290 B2. Arrangement according to the third figure of the invention consists of the active tightening element of the hoisting rope which is a power unit provided with at least one cylinder, a piston moving in the cylinder , flow channeling , a pump acting as an actuator that moves the piston and a fluid reservoir . The real-time feedback information about the tension of the hoisting ropes in the loading situation at the time is arranged to the actuator.

The drawback in this previous embodiment of the patent is that it is not safe and this is what the inventors themselves mentioned about their embodiment in their patent. The reason why it is not safe is that any oil leakage will be dangerous. The second drawback is that the hydraulic circuit necessitates a hydraulic power unit to be exclusively used by the circuit.

Another drawback in traction counterweighted elevators (geared or gearless) which I will eliminate by my inventive hydro traction sheave elevators presented in some of my embodiments is the power consumption in traction counterweighted elevators (geared or gearless) . The motor consumes energy - that may be saved - in spinning when the car is heavily loaded in downward motion and when it is empty or lightly loaded in upward motion. To overcome this, manufacturers made some drives to be operated by the load in reverse as an alternator and often this surplus electrical energy, if it cannot be regenerated, is unwanted and it can be harmful to the electrical motor drive system. When this condition arises the surplus energy can be absorbed by a resistive load into the motor circuit which converts it into heat and at the same time a braking effect is created, which usually is desirable for reasons of safety and protection of the electrical drive system. However, this is expensive.

Moreover, there are some drawbacks in permanent magnet gearless drives that are used for machine roomless elevators for theses drives have so many

disadvantages such as:

1 - They are just used for passenger and service but not for freight.

2- They are applied for just Low to mid rise, 4-25 floors

3- Their typical speeds are just 200-500 fpm

4- They are expensive and take much money to maintain.

The purpose of this invention is to eliminate all the aforementioned drawbacks and to achieve a reliable arrangement of roped hydraulic elevators with and without counterweight for all heights and speeds.

Disclosure of the invention: -

In my inventive embodiments I will try to make hydraulic elevators be used for all heights (low - mid - high and very high rises)

To achieve this, I will use inventive roping arrangements in two of my

embodiments that can apply 7: 1 or 9: 1 ratios in a very simple way. These arrangements will be with or without a counterweight. Another inventive embodiment is a hydro- traction sheave elevator with and without a counterweight wherein the traction sheave is driven by two tiny hydraulic rams that rotate the traction sheave.

I will term the traction sheave driven directly by two tiny hydraulic rams as GEARLESS HYDRO TRACTION. The hydraulic pistons will move at a speed not exceeding 150 - 200 foot per minute for safety considerations and this will be applied for low and mid rises.

The speed of the sheave of gearless hydro-traction sheave elevator can be increased or decreased in a very simple way and this will be by changing the connecting point of the two rams to the traction sheave and this will increase or decrease the diameter. For instance , if the speed of the two pistons is 150 or 200 and we want the sheave to move double the speed of the two pistons ,i.e. in a ratio 2: 1 , then we will connect the two pistons in the half diameter of the traction sheave from the axis of rotation and a full cycle of the two pistons will make two cycles of the traction sheave .In the same way 3: 1 ratio can be achieved ; however bigger ratios will be disadvantageous for this will increase the diameter of the traction sheave

Consequently , for high and very high rises a flat and compact planetary gearbox of the desired gear ratios and one stage ( or multiple stages ) simple planetary gearbox will be sufficient for increasing the speed of the traction sheave while keeping the hydraulic pistons running at a speed not exceeding 150 - 200 foot per minute for safety considerations . I will term the hydro traction sheave equipped with the planetary gearbox as A GEARED HYDRO TRACTION SHEAVE. All the hydro traction sheave elevators will be optionally equipped with a hydraulic shoe brake for safety to stop the traction sheave when it rotates over than usual on the condition that the rope(s) are still intact ,i.e. not cut . The hydro-traction sheave will make it possible for the use of a counterweight like that used in electric traction sheave elevators. Thus, hydro traction sheave elevators (whether gearless or geared) will be competitive to electric traction sheave elevator concerning energy saving. In addition, the hydro traction sheave elevators will be used without counterweight and an inventive safety tensioning device will be applied.

My inventive hydro-traction sheave elevator will save energy - and without any extra expenses - when the car is heavily loaded in downward motion and when it is empty or lightly loaded in upward motion .This will be done by controlling the flow of the hydraulic fluid through the electric flow control valve while the motor will be stopped fully for the potential energy whether of the counterweight or the heavily loaded car will drive the traction sheave and this will move the two pistons of the hydraulic cylinders and by the electric flow valve the movement of the two pistons can be controlled .Thus, this will be an extra safety element in comparison with cable traction elevators ( geared ,gearless) when there is any electric interruption for the electric flow control valve will be equipped with a manual lever to make any ordinary person open the valve and the potential energy will do the work of the electric pump and make the car reach the nearest floor but in traction cable elevators the passengers will be trapped until the maintenance person comes for the electric brake will stop the movement of the traction sheave . To overcome this, a battery or a generator is used to operate the motor at the time of electric interruption to make the elevator car reach the nearest floor but however this is expensive, so it is not widely used. The following comparison will show that:

Power consumption In downward motion In upward motion

when the car is when the car is heavier than the lighter than the counterweight counterweight

My inventive Hydro- The motor stops The motor stops traction totally and the totally and the

Sheave elevators potential energy of potential energy of

the car rotates the the counterweight sheave with the two rotates the sheave pistons. with the two pistons.

Machine roomless and The motor still spins The motor still spins the traditional gearless

and geared elevators

Chart 2. Power consumption comparison between Machine roomless and the traditional gearless and geared elevators and hydro-traction sheave elevators

In some of my inventive embodiments of hydro traction sheave (whether geared or gearless), I will eliminate all the drawbacks of the mrl drives and the following comparison will show that :

E

Ty P nv

Build D

pic Loads on r Disad ir

Elevator Applica ing u

al building i van to safety on type tion Heig t

Spe structures c ges m ht y

eds e en t

Compact Passeng Low 200 M Imposes e High Less

Gearless er, to - 0 all X er safer

Traction Service mid 500 d equipment P cost ec

(MRLs) rise, f e loads on e to 0-

4-25 m r building n maint fri floors a structure si ain en t at 500 fpm V dl e only e y u

s

e Gearless Passeng Low 100 t f No loads on L Cheap Safer

Hydro- er, to mid - 0 building 0 er especi traction Service, rise, 600 d Structure w Maint ally at ec sheave Freight 2-25 fpm e For the c enanc the 0- elevators floors r power unit 0 e time fri a + the St of en t control unit power dl e will be interr y t disposed in uption

0 the

basement or earth h in the shaft quake e s, fire a

v

y u

s

e

Geared Passeng High 450 M No loads L Chea Safer

Hydro- er, rise, - 0 on 0 per espec traction Service, 12- 1,8 d building w Main ially ec sheave

Freight 100+ 00 e structure tenan at the 0- elevators

floors fp r For the c ce time fri

(The

m a power unit 0 of en traction

t + the s powe dl sheave is

equipped e control t r y with one t unit will interr stage _or 0 be uptio two stages disposed n,

- h in the earth planetary

e basement quak gearbox

a or in the es, for

V shaft fire increasing

the y

sheave

speed.) u

s

e Chart 1. Comparison between mrl elevators and my inventive embodiments of gearless and geared hydro-traction sheave elevators

It ought to be noted that the two terms geared and gearless that are used in the naming of my two inventive embodiments: geared and gearless hydro-traction sheave elevators do not mean the exact same terms used with geared and gearless elevators. Whether geared or gearless hydro-traction sheave elevators the power unit utilizes a pump driven by an AC gearless electric motor, which forces oil into the

hydraulic cylinders. In gearless hydro-traction sheave, the two hydraulic pistons which rotate the sheave are connected directly to the sheave while the geared hydro-traction sheave will be equipped with a compact flat planetary gearbox of one stage or two stages to increase the speed of the sheave. Consequently, the hydro-traction gearless traction sheave is slower than the geared one. On the contrary of the two terms used with the traditional cable traction elevators wherein the geared traction elevators are slower in their speeds than the gearless elevators. Moreover, Geared lifts use a reduction gear to reduce the speed of the motor while in gearless lifts the sheave is directly coupled to the motor, i.e. the function and arrangement are different between the two terms in the hydro and non hydro traction sheave elevators.

Furthermore, the use of two tiny cylinders for the traction sheave is very advantageous for these cylinders can be made very strong than the traditional cylinders used in hydraulic elevators and this will be cost effective for their tiny size but in traditional long cylinders, this will be very expensive and the following comparison will show the advantages of the two tiny cylinders over the traditional long cylinders :-

Use

Oil maintena Bucklin safe environm

Type of application Height

leakage nee g ty ent oil

The two Easy to Less Easy Not Safe For freight Can Eco- tiny determi use maintena liable r application rotate friendly cylinder of nee for to that they can be the

s of the And oil their tiny for made of traction

traction lesser size or their bigger sheave

sheave possibili even their tiny diameter - to reach

ty to substitute size for all

happen n is not and increasing heights

expensive they torque of

can be the motor - made with trivial

very cost

strong

and

this

will not

be

expensi

ve

The difficult Mu Difficult Safe Manufactur Limited Just traditio to eh to Liable ing long in their holeless nal long determi use maintain to that cylinders in travel cylinders cylinder ne of for their for big sizes is heights are eco-

And oil long size their expensive and if friendly more and they long they are possibili are size lengthen t to expensive ed they happen if will be

replaced liable to

the

danger

of

buckling

Comparison between the two tiny cylinders of the traction sheave and the traditional long cylinders.

Furthermore , my inventive hydro traction sheave elevators will overcome the problem of the penthouse for the traditional geared and gearless elevators for the power unit and control unit will be disposed either in the pit of the shaft or in a basement adjacent to the shaft .In addition , the hydro traction sheave can be disposed in the pit of the shaft in the same side of the counterweight and this will be cost effective . Moreqver, in one of my embodiments I. will present an arrangement of a

counterweightless hydro traction sheave elevator with a safety adjustable tensioning device. REIF DESCRIPTION OF DRAWINGS :

FIG. 1 illustrates a diagram of a roped hydraulic elevator without a counterweight ( and it can be counterweighted like the embodiment in fig.2 ) with an increasing speed and height unit which achieves a ratio of 7:1 and this ratio can be increased or reduced.

FIG. 2 illustrates a diagram of a roped counterweighted hydraulic elevator with an increasing speed and height unit which achieves a ratio of 9: 1 and this ratio can be increased or decreased.

FIG. 3 illustrates a diagram of the hydraulic circuit of the hydro traction sheave elevator with just one cylinder for simplifying the way of how it works.

FIG. 4 illustrates a diagram of the hydraulic circuit of the hydro traction sheave elevator with two cylinders for illustrating the way . of how they work.

FIG. 5 illustrates a side view of the traction sheave and the arrangement of the two directional flow control valves and a back view of the two cylinders.

FIG. 6 illustrates a cross-sectional view of the traction sheave and the gear that rotates the two gears of the two cams.

FIG. 7 illustrates one side view of the traction sheave and the two cylinders that rotate it.

FIG. 8 illustrates the circuit of the hydraulic shoe brake and the brake parts. FIG. 9 shows a cross-sectional view of the traction sheave and the flyball ball governor. Also, this figure illustrates one hydraulic cylinder connected to the brake drum.

FIG. 10 illustrates a cross-sectional view of the traction sheave 17 and how one hydraulic cylinder is connected to it directly without any emergency hydraulic shoe brake.

FIG. 11 illustrates a cross- sectional view of the traction sheave, the drum emergency brake, the compact planetary gear box and a cylinder connected to it.

FIG. 12 .illustrates the arrangement of the hydro traction sheave with the elevator car and a counterweight.

FIG. 13 illustrates the arrangement of the hydro traction sheave and the adjustable tensioning device in a non counterweighted elevator.

FIG. 14a illustrates the hydraulic circuit of the adjustable tensioning device.

FIG. 14 b illustrates the adjustable tensioning device equipped with a load instead of the spring as a safety element.

FIG. 14 c illustrates a cross sectional view of the shaping of the upper piston rod 4 wherein .the two sides of its cylindrical shape are cut flat so as to make the load 2 keep still and does not go round .

DETAILED DESCRIPTION OF EXAMPLE EMBODIMENTS

A hydraulic roped elevator according to FIG.1 includes a car 2 slidingly engaged with guide rails 32 for vertical movement in the hoistway. This hydraulic roped elevator 1 also includes an increasing speed and height unit 4 which consists of : 2 single hydraulic cylinders 5 and 6 connected to the pump ( which is not shown here ) . The crosshead 9 is attached to the distal ends of the two pistons 7 and 8 and is fastened with two pins 35, 36. In addition, there are three diverting pulleys 10, 11, 12 disposed on the crosshead 9. Crosshead 9 is slidingly engaged with guide rails 22. Furthermore, there are four diverting pulleys 13, 14, 15, 34 disposed at the end of the shaft. The rope 17 (or belt) will be fastened from one of its ends 18 to the lower part of the crosshead 9. From fixing point 18 the rope 17 goes downward to the diverting pulley 13 and then upward to the diverting pulley 10 and from this diverting pulley 10 , the rope 17 goes downward to the diverting pulley 14 . From diverting pulley 14 , the rope 17 goes upward to diverting pulley 1 1 and then downward to diverting pulley 15 and from this pulley 15 , the rope will go upward to pass around diverting pulley 12 . Having passed around this pulley, the rope will go downward to diverting pulley 34 and then upward to pass over the two diverting pulleys 19, 20 to finally be fixed to the car.

The rope (or belt) can be fixed to the center of gravity of the car 2 and then diverting pulley 20 will be replaced by diverting pulley 21 which will be disposed at the top of the shaft. After having passed around diverting pulley 21, the rope 17 will be fixed to the center of the car 2. It's worthy noting that in case of using diverting pulleys 19 and 20 or 19 and 21 , each two pulleys will be aligned to each other.

The elevator car 2 and the crosshead 9 travel in the elevator shaft along guide rails : 32 for the elevator car and 22 for the crosshead 9. The elevator car 2 is suspended on the guide rails in a manner called rucksack suspension, which means that the elevator car 2 and its supporting structures are almost entirely on one side of the plane between the elevator guide rails 32. The elevator car and crosshead guide rails 32, 22 are

implemented as an integrated rail unit having guide surfaces for guiding the elevator car 2 and the crosshead 9 as in fig.1. Furthermore, it is an option for the use of guide rails at two sides of the car 2 for guiding the elevator car 2 instead of guide rails 32 in rucksack suspension.

In holed hydraulic cylinders, the cylinders 5, 6 which push the crosshead 9 will be in the ground and this will be an advantage for then the two pistons 7, 8 can be directly disposed under the elevator car 2 and pushing the crosshead 9 on the same rail guides 32 of the elevator car 2 letting just sufficient space for the rope 17 to move . This will give a merit to the size of the elevator car 2 which will be bigger.

To make the car 2 move upwards, the pump (not shown here) will urge fluid into the two cylinders 5 and 6 causing the two pistons 7 and 8 move upwards. The two pistons 7 and 8 will push upwards crosshead 9 and the three diverting pulleys 10, 11, 12. Thus , rope ( or belt ) 17 will be drawn and the diverting pulleys 10, 11 , 12 and 13 , 14 , 15 , 34 will facilitate its movement . The car 2 will move upwards with a ratio of 7: 1 ; i.e. if the two pistons 7 and 8 move upwards to a distance of 1 meter , the car 2 will move 7 meters and this will make the car 2 faster 7 times than the two pistons 7 and 8 .

Similarly, the ratio 7: 1 can be decreased by decreasing the number of pulleys on the crosshead 9 and down the shaft and vice versa .

In downward motion , the hydraulic valve ( not shown ) will be opened letting hydraulic oil flow to the oil tank ( not shown here ) and the load of the car 2 will draw rope 17 and crosshead 9 will move downwards pushing the two pistons 7 and 8 into their cylinders 6,5 .

The advantages of this embodiment can be shown as follows :-

1- 7: 1 roping between the car 2 and the two pistons 7, 8 enables the car 2 to move at 7 times faster than the two hydraulic pistons 7, 8.

2- Roping ratios can be decreased or increased easily by decreasing or increasing the number of the diverting pulleys on the crosshead 9 and at the bottom of the hoistway.

3- This embodiment will make the hydraulic cylinders shorter and this will be cost effective. 4- Speed of the car in downward and upward motion will be increased although the movement of the pistons will be very slow and this will be very safe.

5- This embodiment will enable roped hydraulic elevators reach higher heights than before; for instance if the standard heights reached by hydraulic elevators types are as follows:

Then with a ratio of 7: 1 as in fig.l, the travel heights and possible maximum stops will be as follows:

Thus, this embodiment presented in fig.l will make hydraulic elevators reach low, mid, high, and very high rises with maximum speeds than ever.

And if the ratio will be 9: 1 as in fig. 2, the maximum heights and stops according to hydraulic elevator type will be as follows:

Maximum stops Travel height Hydraulic elevator type

27 stops 180 ft Roped Holeless hydraulic

45 stops 396 ft Roped Telescopic holeless

hydraulic

63 stops 450 ft Roped Holed hydraulic Fig.2 is the same like fig.1 but with the addition of a counterweight 31 and the ratio is 9: 1. This counterweight will be disposed over the crosshead 9 and it will be connected to crosshead 9 by the rope 23. The movement of the rope 23 will be facilitated by diverting pulleys 24, 25, 27, 28 which will be disposed in the shaft and the movable pulley 37 disposed on the center of the counterweight 31. The

counterweight 31 and the crosshead 9 will be roped in 1 : 1 relationship ; but if we used the two movable pulleys 29 and 30 which will be disposed on top of both sides of the counterweight 31 , the roping will be 2: 1 ; i.e. if the crosshead 9 moves 1 meter , the counterweight 31 will move for a half meter and this will decrease the traveling distance .

It ^" is worthy noting that the counterweight 31 will slidingly move using the same guide rails 22 that will be used by crosshead 9 and this is because the traveling distance will be very short for both the counterweight 31 and the two pistons 7,8 . For instance if there is a building consisting of 9 floors, the two pistons 7, 8 will move upward or downward for just 1 floor causing the counterweight 31 to move for the same distance if it is roped 1 : 1 with the crosshead 9 and for half floor if it is roped 2: 1 with crosshead 9. Thus, they can be disposed on top of each other taking into consideration a safety distance.

Fig.3 presents a diagrammatic illustration of how the hydro traction sheave works. The motor 1 will run the pump 2 which will pump up the hydraulic fluid which comes from the fluid tank 3 through pipe 4 passing through the oil filter 5. The oil will be pumped through pipe 6 to flow across check valve 7. The pressure relief valve 27 is connected to the circuit through pipe 28 and it opens when the pressure is too high letting fluid pass through pipe 29 to the fluid reservoir 3. The check valve 30 prevents fluid to return back to the fluid reservoir 3. Then fluid passes through the flow control valve 19 which controls the magnitude of liquid flow and this valve will be equipped with a manual lever for opening it manually if the electric current is interrupted for safety consideration. After that the fluid passes through the reverse flow valve 20 which can reverse the fluid pumping direction whether up or down the piston 22 in the cylinder 21 according to requirement and this makes the piston 22 reverses the rotation of the traction sheave 17 for upward or down ward motion .

The. directional control valve unit 9 which is disposed on the other face of the traction sheave 17 and for illustration it is drawn away from its placement and the arrow 18 shows its original disposition at the other side of the traction sheave 17 . This valve unit 9 consists of the body valve 10, the spring 1 1 and the valve push rod 14 which retracts and extends according to the rotational movement of the cam 12. The cam 12 is run by the traction sheave axis of rotation 13; however, at least two cams will be used to control the movement of two cylinders to rotate the traction sheave smoothly as in fig. 5. The directional control valve unit 9 controls the flow of fluid pumping whether to pipe 15 or pipe 16 to the double acting cylinder 21 which is connected to the traction sheave 17 in the point 25 and this makes the piston rod 26 rotates the traction sheave 17. The cylinder 21 is fastened by the pin 23 in the housing of the sheave 17.

When fluid is pumped up piston 22 causing it to extend to the end of the cylinder 21, the piston rod 26 rotates the traction sheave 17 a half cycle. Then, the cam 12 which is run by the traction sheave axis of rotation 13 reverses the directional control valve 9 making the fluid reverse its direction to flow under the piston 22. The piston 22 retracts pushing the fluid to flow again to the fluid reservoir 3 through pipe 8. When the piston 22 retracts, the traction sheave 17 completes its rotation.

The rope 24 (or belt) is drawn by the traction sheave 17. The elevator car and counterweight -which are not shown here - will be fastened to this rope.

This system is energy effective and safe at the same time especially when the electric current is interrupted for the elevator car can reach the nearest floor without electric energy ; for instance if the car is empty or its load is lighter than the counterweight and it is in a lower floor , then it can travel upward without any electric energy and the motor 1 will stop totally , just with the potential energy of the counterweight and vice versa if the car is heavier than the counterweight in downward motion . The potential energy of the car will run the sheave 17 , but this will be prevented by the piston 22 which is connected to the sheave 17 by its rod 26 in the point 25 for the hydraulic fluid up and down the piston will stop the piston from moving as long as the control flow valve 19 is locked . When the control flow valve 19 is opened, the traction sheave 19 will make the piston 22 retract and extend and this motion will produce a sucking effect like a water pump of fluid from the reservoir 3 and this sucking effect will open the check valve 30 and the flow control valve 19 will control the magnitude of fluid to control speed of rotation of the traction sheave 17.

Fig.4 illustrates a diagram of a hydro traction sheave elevator circuit but with 2 cylinders 21, 31 connected in the same point 25 to the traction sheave 17 but they are disposed with different axes and with two directional control valve units 9, 32 and this to achieve smooth rotation of the traction sheave.

In fig.4 the other cylinder 31 will work in the same principle like cylinder 21 and the two pipes 33 , 34 will permit fluid to pass up and down the piston of the cylinder like the qther cylinder 21 and pipe 35 will let fluid to return back to reservoir 3 .

Fig.5 illustrates how the two directional control valves units 9, 32 are disposed at the other side of the traction sheave 17 which is disposed in the housing 36. The gear 37 which is fastened to the center of rotation of the sheave 17 rotates the two gears 34a, 34b that rotate the two cams 12a, 12b in their turn for they are connected to each other . Each cam with its gear will be one piece and they will be disposed on the metal frame of the sheave housing.

Fig. 6 illustrates a cross sectional view of the sheave 17 and 2 traction ropes 24 , gear 37 that rotates the two cams ^' gears 38 a ,38 b and the two cams 12a, 12b .

Fig. 7 illustrates the other side of the sheave 17 with the traction ropes 24; the two cylinders 21, 31 ; the metal housing 36 to which the two cylinders are connected by two pins 23a, 23b. Fig. 8 illustrates the emergency shoe brake with its hydraulic circuit for traction sheave 17 which will stop the sheave 17 when there is any failure in the hydraulic circuit that causes uncontrollable rotation of the sheave 17 on the condition that the rope(s) are still intact, i.e. not cut. The brake drum 36 - to which the rods of the two pistons will be connected - is rotationally connected with the traction sheave 17 (not shown). Two brake levers 4 and 5 are pivotally mounted on a brake housing 6 at lower ends 2 and 3 respectively. Brake shoes 7 and 8 with brake linings are immovably fastened to the brake levers 4 and 5. Upper ends 9 and 10 of the brake levers 4 and 5 are connected by way of brake springs 1 1 and 12 and tie rods 13 and

This emergency brake will be set by opening the valve 18 which will let the hydraulic fluid to flow from the pump (not shown) through pipe 22 while the flow control valve 19 will be closed . The conduit of the brake will be taken after the pump 2 and after check valve 7 as in the hydraulic circuit in fig.3

When the pump operates, the fluid will press the two pistons 16, 17 in the cylinder 15 and the two springs 1 1, 12 .This action will push the brake levers 4, 5 with their shoes 7, 8 making the shoes not touching the drum 1. The pressure relief valve 20 will allow fluid to go to the reservoir 3 when the fluid pressure is too high in the brake circuit while pumping fluid into the brake.

The fluid pressure sensor 44 in the brake circuit will control automatically the setting of the brake: it will control the opening and closing of the pump (of course the operation of the pump is controlled by the control unit as well) and valve 18. This pressure sensor consists of a cylinder 40, a piston 42, a spring 41 , a rod 43 connected to the piston 42 and a non - returnable electric switch 39 for safety. When the hydraulic pressure in the brake circuit increases after setting the brake , it will press the piston 42 and the spring 41 under which causing the rod 43 to move pressing the non - returnable electric switch 39 and this switch will stop the motor and close the electric valve 18 . The electric switch 39 is non - returnable for safety consideration for when the fluid is released in emergency braking or if there is any oil leakage in the brake circuit , the piston rod 43 will stop pressing the electric switch 39 for it will return back by the spring 41 . This action can make the electric switch 39 re-open the valve 18 and re - operate the pump to re-set the brake and this will be very dangerous , so it must be non returnable .

In emergency, valve 21 will open automatically when the rotation of the traction sheave 17 (not shown) is over than usual letting the fluid to flow to the fluid reservoir 3 and the two springs 11, 12 will push the two brake levers 4, 5 toward the rotating drum 36 to stop it. The apparatus which will control the opening of the valve 21 is an over speed fly ball governor 45 which is shown diagrammatically in fig.8

Fig.9 shows a cross sectional view of the traction sheave 17 and the traction ropes 24. The gear 33 which is fastened to the traction sheave will rotate gear 34 which is connected to the fly ball governor 35. When the flyball governor rotates over than usual, it will open the valve 21 that will pass brake fluid to the reservoir 3. This action will make (as shown in fig.9) the two springs 1 1, 12 push the two brake levers 4, 5 toward the rotating drum 36 to stop it.

The fly ball governor 35 can be disposed at the lower diverting sheave of elevator governor -which is placed in the elevator pit- to rotate its mechanism.

For extra safety, f g. 8 shows an optional parallel valve 23 to the valve 21 and it will be controlled electrically. There will be an over speed sensor disposed on the traction sheave 17 and the measurements data from this sensor will be sent to a control element - that will be part of the sensor or the control unit of the elevator - for processing measurements data for sending the electric signal to the valve 23 to open when the traction sheave rotates over than usual. This valve will be more accurate than the mechanically opened valve 21 ; however they will do the same task for more safety.

Fig. 10 illustrates a cross sectional view of the elevator traction sheave 17 with the traction ropes 24 (at least two for safety) disposed on the base of the housing 6. It's shown that one of the two pistons 31 is connected directly to the traction sheave 17. In this figure there is no emergency traction sheave brake.

Fig. 1 1 illustrates a cross sectional view of the elevator traction sheave 17 with the traction ropes 24 (at least two for safety) disposed on the base of the housing 6. The brake drum 36 in this figure is adjacent to the traction sheave 17 to seem as part of it and it can be so. In this figure there will be one stage - or multiple stages - planetary gearbox 37 to achieve higher gear ratios as desired. The planetary gearbox 37 is flat, compact sized and efficient. The two cylinders - one of them 31 is shown - will be connected to the planetary gearbox 37 to rotate the gearbox that will in turn rotate the traction sheave 17 with faster ratios. By adding this planetary gearbox 37 we will overcome the operating low speed of the two hydraulic cylinders and the traction hydraulic sheave 17 will be suitable for all high rises.

Fig. 12 illustrates a diagram of the roping arrangement of the hydro traction sheave 17, the counterweight 1 and the car2. As in the diagram the sheave 17 will be disposed beside the counterweight 1 in the same side in the shaft. One part of the rope 24a will go upward to pass over the diverting sheaves 5, 6 until to be fastened to the top center of the car 2. The other part of the rope 24b will go upward to pass over the diverting sheaves 7, 8 and then it will go downward till it will be fixed to the top center of the counterweight 1. This roping arrangement is 1 : 1 and roping can be 2: 1 if we add a movable diverting sheave 9 over the counterweight 1 and the rope 24b will go downward this sheave and then upward to be fixed in top of point 10 of the shaft . According to 2: 1 roping, the counterweight 1 will travel half the distance of the car 2. As shown in the same diagram an optional diverting sheave 1 1 can be disposed on top of the sheave 17 and the rope 24b will pass under it and this to achieve more traction around the sheave 17 and to give more space for the movement of the counterweight 1. It will be noticed that the diverting sheave7 will be realigned then with the diverting sheave 1 1. In this diagram there is an overspeed governor 3 and the diverting sheave governor 4 disposed in the pit can be used for operating the mechanism of the flyball governor 45 used for opening the valve 21 of the emergency brake used as a safety device.

Fig.13 illustrates an elevator of a hydro traction sheave 17 without a counterweight and with a safety adjustable tensioning device to achieve the proper traction around the sheave 17.The roping arrangement will be as follows: The traction sheave 17 will be disposed in the pit of the shaft. One part of the traction rope 24a will go upward from the traction sheave 17 to pass over the diverting sheave 1 which will be disposed at the top of the shaft and then downward to pass under the two diverting sheaves 2,3 which will be fixed at the top part of the car 8 . Then, the rope 24a will go upward to be fixed in the point 4 at the top of the shaft. The other part of the rope 24b will go upward to pass over the two diverting sheaves 6, 5 which will be disposed down the car 8 and then downward to be fixed in the rod of the adjustable safety tensioning device 7 .

Fig.14a illustrates the active tightening element 7 of the hoisting rope 24. This tightening element consists of at least one cylinder 5, a piston 1 moving in the cylinder 5 and the hoisting rope 24b will be fastened to the top of its rod 4. There will be a spring 2 over the piston 1 in the cylinder which is calculated to achieve the maximum tension of the hoisting rope 24b by pushing the piston 1 downward and this will achieve safety if there is any oil leakage. This adjustable safety device will use the motor driven pump 2 ( not shown here ) of the two pistons of the traction sheave 17 and the conduit 10 will be connected to the pump 2 after check valve 7 ( as shown in fig.4 ) . Valve 9 will be normally closed and it will be opened by the control element to pass fluid from the pump2 to cylinder 3 when required to decrease pressure of the spring 2 on the rope 24b. There will be an over pressure relief valve 6 connected to conduit 10 by pipe 12 and is set at a predetermined value to assure that the minimum pressure applied by the spring 2 on the rope 24b fastened to the rod 4 is not reduced below a predetermined value . In addition, a normally closed solenoid valve 13 will be connected to pipe 10 and it will open when there is any power failure letting pressurized fluid to return back to reservoir 3 for safety consideration. Consequently, the spring 2 will push the piston 1 and its rod 4 to its maximum .This will produce maximum tension of the rope 24b tied to the rod 4.

There will be a car load weighing device and at least one tension sensor which will send their measurements to a control element that will be connected to the pump to operate it when .needed to increase fluid pressure. Also, the control element will control the solenoid valve 13 to open it to reduce pressure under the piston 1 to increase the tension of the rope 24 b when needed. The control element can be part of the measuring device or devices or can be disposed in the control unit as part of it.

Thus, according to measurements sent from the load weighing device and at least one tension sensor , the control element will either increase the fluid pressure under the piston 1 to decrease the tension of the rope 24b by opening the valve 9 and operating the pump to pump over more oil and then closing the valve 9 and the pump or to decrease the fluid pressure to increase the tension of the rope 24b by opening solenoid valve 13 to let the fluid pass to reservoir 3 . This process will be so quick that the arrival or departure of a single passenger maybe counteracted immediately even before a second passenger arrives or departs in many cases.

Fig.14 b is the same like fig.14a but with the substitution of the spring 2 by the load 2 and the load as the spring will be calculated to achieve maximum pressure to hoisting rope 24. The piston rod 6 will connect the load 2. The tensioning device 7 will be fastened to the wall of the shaft by the connection 14. The same hydraulic circuit will do the same function as in fig.14a.

Fig.14 c shows a cross sectional view of the shaping of the upper piston rod 4 in fig.14 a in the cylinder 5 where the two sides of its cylindrical shape are cut flat so as to make load 2 keep still and does not go round and two guide rails can be fastened at both sides of the load 2 to do the same function .

Variations and modifications to the disclosed examples may become apparent to those skilled in the art that do not necessarily depart from the essence of the invention.