RU2238444C2 - Distribution valve unit of hydraulically driven elevator - Google Patents

Abstract

FIELD: systems for controlling rising and descending of cabin of hydraulically driven elevator.

SUBSTANCE: unit includes two distributing valves for regulating oil flow for hydraulic system fed from tank to rising cylinder for driving cabin of elevator and (or) from said rising cylinder to tank. When cabin moves upwards oil for hydraulic system is fed by means of pump driven by electric motor from said tank through distributing valves to rising cylinder. When cabin moves downwards oil for hydraulic system through unit of distributing valves is fed to reservoir and pump is not energized. According to invention unit of distributing valves has in addition single controlled distributing valve that operates as non-return valve and also as proportionally controlled hydraulic distributor. All distributing valves have one common flow limiting member that may be shifted relative to seat. Said flow limiting member is subjected to action of return spring and also to action of additional valve driven by means of electrically selected proportionally controlled magnet.

EFFECT: simplified design, reduced cost of making unit having no regulation members.

18 cl, 18 dwg

Description

The invention relates to a control valve block of an elevator with a hydraulic actuator in accordance with the introductory part of claim 1.

Known blocks of control valves that are used to influence the oil flow for hydraulic systems circulating between the pump or oil tank and the power cylinder, with the aim of directly or indirectly driving the elevator car.

From US patent US-A5,040,639, a control valve block of the type mentioned in the introduction of claim 1 is known. It includes three auxiliary control valves, as well as a check valve, the open state of which is monitored using a location indicator. In addition, in addition to fixed chokes, it also has a number of control elements.

From European patent EP-A2-0964163, a similar block of control valves is known, characterized by a significantly more complex design and, in addition to four main control valves and three auxiliary valves, includes a number of mechanical control elements.

The basis of the present invention is the task of creating a block of control valves, characterized by a simple design and not having control elements. Due to this, production costs are reduced, and installation does not require laborious adjustment operations.

The problem is solved in that in the block of the distribution valves of the elevator with a hydraulic actuator, including distribution valves and auxiliary valves, with which they regulate the flow of oil for the hydraulic system coming from the tank into the lifting cylinder, which drives the elevator car, and / or from said lifting cylinder to said tank, in which the upward movement of said elevator car is ensured due to the fact that said hydraulic oil from said tank is supplied to said lifting cylinder through said distribution valve block by means of a pump driven by an electric motor, and the downward movement of said elevator car is ensured by the fact that said hydraulic oil is supplied through said distribution valve block to said tank, in which downward movement of said cabin the elevator is controlled by one single controlled distribution valve, acting as a non-return valve, as well as as a directional control valve, and the upward movement of the said elevator car is controlled by one single controllable control valve acting as a non-return valve, and also as a proportional control valve, according to the invention, the force of said auxiliary valve of said control valve, which controls the downward movement, transmits the piston, which pushes the control spring by means of a pusher the main valve to the counter-piston, which, with the help of a pusher attached to it, moves the flow restrictor, and the force yanutogo auxiliary valve of said control valve controlling the upward movement, the piston passes by a pusher pressing spring adjusting the main valve to the flow limiter is rigidly attached to a pusher via kontrporshnyu.

In accordance with one embodiment of the invention, each of said distribution valves has one single flow restrictor capable of displacing relative to the seat.

In another embodiment, the return flow spring acts on said flow restrictor as well as an auxiliary valve actuated by a proportionally controlled electrically selectable magnet.

It is advisable that in the process of controlling the upward movement, the return spring and the auxiliary valve of said distribution valve act in the same way on the flow restrictor in the direction of locking of the valve.

According to one embodiment of the invention, in the upward movement control process, the return spring acts on the flow restrictor in the locking direction, while the auxiliary valve acts in the unlocking direction.

In another embodiment of the invention, said flow restrictor of said downstream control valve and said upstream flow restrictor of the same shape and dimensions.

It is advisable that the diameter of said counter-piston is equal to the diameter of said flow restrictor.

It is advisable that the diameter of said counter-piston is equal to the diameter of said flow restrictor.

In yet another embodiment of the invention, a groove extends around the outer circumference of said piston, in which an elastic seal is placed.

In another embodiment of the invention, the surface of said counter-piston facing said flow restrictor is in the form of a truncated cone.

It is highly advisable that said flow restrictors be formed by a base and an adjacent cylinder, in the surface of which there are openings.

At least a portion of said openings is V-shaped.

At least a portion of said openings is bell-shaped.

Mentioned holes change in steps.

In one embodiment of the invention, there is a means by which the lifting of said pistons is limited.

In another embodiment of the invention, a trajectory restriction is provided by a snap ring inserted into one of several annular grooves (95) extending along the cylindrical inner wall of the adjustment compartments.

In yet another embodiment of the invention, a cylindrical retaining ring may be inserted into said adjustment compartment, the outer diameter of which is slightly inferior to the diameter of said adjustment compartment, and the length of which determines the restriction of lift.

The invention will now be described with reference to the drawings, by way of example only, in which:

figure 1 schematically shows an elevator with a hydraulic drive and an adjustment body;

figure 2 shows a schematic top view of a block of control valves;

figure 3 shows the same block of control valves in the case when the elevator with a hydraulic drive moves up;

figure 4 shows a view similar to that of figure 3, but in the case when the elevator moves down;

5 shows a flow restrictor with a counter piston and a pusher;

figure 6 shows an embodiment of a counter piston;

7 shows a counter-piston element;

on Fig-11 shows a modification of the flow limiter;

on Fig and 13 depict modifications of the restriction of the rise;

Fig.14 shows a piston element;

on Fig shows the surface of the body of the flow limiter;

Figures 16 and 17 show cross sections of a flow restrictor;

Fig. 18 shows a particular embodiment of an opening in a flow restrictor.

Figure 1 illustrates an elevator car with a hydraulic drive, driven by a lifting piston 2. Said lifting piston 2 together with the lifting cylinder 3 forms a known hydraulic actuator. A cylinder line 4 is connected to such a hydraulic actuator, through which oil is supplied for the hydraulic system. The other end of said cylinder line 4 is connected to a first control valve 5, which combines at least the functions of a proportional control valve and a check valve. Due to this, it acts as a valve with proportional control, or as a check valve, depending on which function of the control valve 5 is selected, which will be described later. The proportional control function of the valve can be provided in a known manner using a main valve and an auxiliary valve, wherein said auxiliary valve is actuated by an electric actuator, for example, a proportional magnet. The non-return valve in the locked state holds the elevator car 1 in the corresponding position.

Through a pump line 8, in which a pressure pulsation absorber 9 can be installed, said control valve 5 is connected to a pump 10 by which hydraulic oil is supplied from the oil tank 11 to said hydraulic actuator. Said pump is driven by an electric motor 12 to which a current supply element 13 is connected. In said pump line 8, pressure P _p prevails.

Between said dispensing valve 5 and said tank 11 there is an additional line containing hydraulic oil, namely a return line 14 in which the second dispensing valve 15 is located. If the pressure P _p exceeds a predetermined threshold value, said dispensing valve 15 provides oil return for hydraulic system from said pump 10 to said tank with almost no resistance. Due to this, said pressure P _p cannot substantially exceed said threshold value. Now, said threshold value can be changed by an electrical signal so that said control valve 15 can assume the function of regulating pressure in the same way as a known proportional valve. To perform this function, as in the case of a proportional valve, it is also possible in a known manner to return to the main valve and the auxiliary valve driven by a proportional magnet with electric selectivity.

In said line 4, at the distribution valve 5 itself, or preferably directly at the corresponding terminal of said distribution valve 5, there is a load pressure sensor 18 connected to the adjustment body 20 via the first measuring line 19. Thus, said adjustment body 20 for controlling said elevator with hydraulically driven, is able to recognize what pressure P _z prevails in said cylinder line 4. In the case where the elevator car is at rest, said pressure P _z represents the load of said elevator car 1. By using said pressure P _z, it is possible to influence the control and adjustment operations and set the operating conditions. Said adjustment body 20 may also consist of several control and adjustment units.

In said cylinder line 4, it is also preferable, directly at the corresponding terminal of said control valve 5 or at the control valve 5 itself, that a temperature sensor 21 is preferably connected to said adjustment body 20 via a second measuring line 22. Since the viscosity coefficient of the hydraulic oil obviously changes together with the temperature, the control of the mentioned hydraulic elevator and the adjustment of its operation can undoubtedly be improved, eu whether the temperature of the aforementioned hydraulic oil will be included as one of the parameters in the control and adjustment operation.

Preferably, an additional pressure sensor is provided, namely a pump pressure sensor 23 that detects a pressure P _p in said pump line 8 and is preferably located directly at the corresponding terminal of said pump line 8 of said control valve 5. Said pump pressure sensor 23 also transmits measured values via an additional measurement line 24 to said adjusting body 20.

The first control line 25 leads to said control valve 5 from said control body 20. Due to this, said control valve 5 is controlled electrically by said adjusting body 20. In addition, a second control line 26 leads to said control valve 15, whereby it is also controlled by said adjustment body 20. An additional third control line 27 leads from said adjusting member 20 to said current supply element 13, thereby turning motor 12 on and off, and if necessary, said adjusting member 20 controls the speed of motor 12 and thereby the volume supplied by said pump 10.

By addressing said control valves 5 and 15 to said control body 20, the functional behavior of said control valves 5 and 15 is determined. If said control valves 5 and 15 are not selected by said control body 20, both control valves 5 and 15 act in principle as a check valve with adjustable offset. If said control valves 5 and 15 are selected by a control signal, they act as proportional control valves.

In accordance with the present invention, both control valves 5 and 15 are combined in a control valve unit 28, which is indicated in the drawings by a dashed line surrounding both control valves 5 and 15. This reduces the cost of installing said hydraulic elevator at the construction site. In accordance with the general inventive concept, both control valves 5 and 15 are similar and consist of identical components, which gives a number of advantages, which will be described later.

Prior to a detailed disclosure of the invention, the principle of its operation will be explained. When the said elevator car 1 is at rest, it is important that the control valve 5 is locked, which, as already indicated, is now achieved due to the fact that it does not receive a control signal from the said adjustment body 20 via the said control line 25, i.e. . acts as a check valve. The control valve 15 may also be locked, however this is not always necessary. Thus, it is possible that when the above-mentioned elevator car is at rest, the pump 10 will also work, i.e. supply oil to the hydraulic system, and that, despite this, the mentioned hydraulic oil through the said control valve 15 will flow back to the tank 11. However, since, as a rule, both control valves 5 and 15 do not receive at rest control signals from the said adjustment body 20, in both cases they can perform the function of a check valve.

An unselected electrically mentioned control valve 5 is automatically shut off by the pressure P _z created by said elevator car 1 when said pressure P _z exceeds the pressure P _p . As already indicated, under such a condition, the load pressure sensor 18 will detect the load created by said elevator car 1. Due to this, the size of the payload of said elevator car 1 is determined, which is transmitted to said adjustment body 20. Thus, said adjustment body 20 is able to recognize whether said elevator car 1 has a payload or not, and also determine a load amount.

When the above-mentioned elevator car 1 moves upward, said adjustment body 20, via the control line 27, first drives the current-supplying element 13, and thereby rotates the electric motor 12, which drives the oil supply pump for the hydraulic system. This increases the pressure P _p in said pump line 8. As soon as said pressure P _p exceeds a value corresponding to the displacement of said check valve of said control valve 15, said check valve of said control valve 15 opens, as a result of which said pressure P _p does not initially may exceed the mentioned value. If the mentioned value, which usually happens, turns out to be lower than the pressure P _z in the mentioned cylinder line 4, the said control valve 5 will remain locked and the hydraulic oil will not enter the said cylinder line 4. Thus, turning on said pump 10, however, does not drive the elevator car 1, since all hydraulic oil supplied by said pump 10, in this case, is returned to said tank 11 through the control valve 15. Now, in order to in order to drive said elevator car 1, said regulating member 20 can, according to said control line 26, control the function of the directional control valve with proportional control of said control valve 15 so as to establish s increased hydraulic resistance in said pilot valve 15.

Due to this, the said pressure P _r increases so that through the distribution valve 5 into the aforementioned line 4 of the cylinder could receive the necessary amount of oil for the hydraulic system. A portion of the hydraulic oil supplied by said sediment 10 through said distribution valve 15 is fed back to said tank 11. A portion of the oil supplied by said sediment 10 of hydraulic oil is not fed through said distribution valve 15 back into said tank 11 through said distribution valve 5, under the influence of the prevailing pressure difference acting as a check valve, enters the above-mentioned line 4 of the cylinder, whereby the elevator car rises. This ensures continuous control of the flow of said hydraulic oil into said lifting cylinder 3 without the need to control the speed of said pump 10. The only requirement is that the design of said pump 10 must be such that it is capable of supplying an amount of hydraulic oil, providing the maximum speed of the aforementioned elevator car at the maximum back pressure that can occur at rated speed, p This should also take into account normal redundancy factors and other structural margins.

Figure 2-4 shows a first embodiment of a control valve unit 28 according to the present invention. FIG. 2 shows a basic state in which none of the control valves 5 and 15 of the control valve unit 28 are selected. Figure 3 shows the state in which the elevator car 1 moves up (figure 1), and figure 4 shows the state when the car moves down.

2 to 4, said control valve block 28 is a combination of said control valves 5 and 15. At the top, said control valve 5 is shown, and at the bottom is a control valve 15. FIG. 4 shows the connection of said control valve block 28 with said line 4 (Fig. 1), Fig. 8 shows a connection with said pump line 8, and Fig. 14 shows a connection with said return line 14. The pressures P _z and P _p prevailing in the connection regions mentioned earlier herein and which can be determined by the pressure sensors not shown. Each of the distribution valves 5 and 15 consists of a main valve and an auxiliary valve, again actuated by a proportional magnet.

Said control valve block 28 consists of two housing elements, namely, a first housing element 30 in which the main valves of said control valves 5 and 15 are placed, and a second housing element 31 in which auxiliary valves 100 and 101 are placed. Said housing element 31, in turn, it can be a two-part element, each part of which serves as its own body of said auxiliary valves 100, 101. Connected to each of said auxiliary valves 100, 101 the proportional magnet, namely the proportional magnet 102 is connected to the auxiliary valve 100, and the proportional magnet 103 is connected to the auxiliary valve 101. Said proportional magnets 102 and 103 can be selected by the adjustment body 20 (Fig. 1) along the control line 25 and / or 26, respectively .

Said housing element 30 has several compartments. The first compartment is called the 32 cylinder compartment. Since it is followed by line 4 of the cylinder (FIG. 1), for this reason, the corresponding connection is indicated by [4]. The second compartment is called the pump compartment 33, followed by the aforementioned pump line 8, and their connection is indicated by the position [8]. Another compartment is called the return compartment 34, followed by the mentioned return line 14, and their connection, respectively, is indicated by the position [14].

In the hole between said cylinder compartment 32 and said pump compartment 33, there is a first throttle element 35, together with the first valve seat 36, forming the main valve of said control valve 5 in said housing element 30. According to the present invention, said main valve of said control valve 5 is is the main device that directly affects the oil flow for the hydraulic system coming from the said lifting cylinder 3 (Fig. 1) and into . For the sake of completeness, it should be noted that, depending on the choice of said auxiliary valve 100, a small part of the flow may also pass through it. Said main valve of said control valve 5 also performs the function of a check valve and at the same time the function of a directional control valve with proportional control, which will be explained later. When performing the function of a non-return valve, it meets the safety requirements established by the relevant EN standards, so that no additional safety valve is required.

The return spring 37 activates the flow restrictor 35. With said return spring 37, the main valve remains locked until the pressure P _p in said pump compartment 33 exceeds the pressure P _z in said cylinder compartment. This happens, for example, when the aforementioned pump (Fig. 1) does not work, and the elevator car 1 (Fig. 1) is at rest.

At the same time, said flow restrictor 35 is influenced by adjusting devices driven by the selection of said valve 100. The said adjusting devices include a counter-piston 38 with a pusher 39 attached thereto. The said counter-piston 38 is capable of displacing in the guide region 40 located inside said body member 30. Said counter piston 38 is actuated by said auxiliary valve 100. This is as follows. Mentioned proportional magnet 102 in a known manner through the solenoid plunger 41 moves the auxiliary piston 43, compressing the auxiliary adjusting spring 42. As a result of the movement of the said auxiliary piston 43 in the pressure compartment 44 in the control system creates a pressure P _x . Said pressure P _x depends on the movement of said auxiliary piston 43 and is thereby also determined by said auxiliary control spring 42. Since said auxiliary valve 100 determines the pressure P _z in said cylinder compartment 32 by means of the connecting channel 45, and also determines the prevailing pressure by means of the second connecting channel 46 pressure in said return compartment 34, no adjusting devices are required to set the desired pressure P _x in the control system .

Said auxiliary valve 100 regulates said pressure P _x , which is functionally dependent on the pressures in the cylinder compartment 32 and the return compartment 34, as well as on the lift of the auxiliary valve 43, which is also determined by the choice of said auxiliary valve 100.

Due to the pressure P _x, the piston 48 is displaced in the adjustment compartment 47. Said piston 48 is supported on said housing element 30 through an adjustment spring 49 of the main valve. The movement of said piston 48 by means of a pusher 50 is communicated to said counter-piston 38. Thus, said main valve adjustment spring 49 acts, on the one hand, as a reset spring of said piston 48 and, on the other hand, as an adjustment spring of said main valve of said distribution valve 5. In accordance with the invention, in this case also, no adjustment devices are required.

Thus, in accordance with the invention, to provide the functions of a non-return valve and a directional control valve, only one flow restrictor 35 is required, which together with said valve seat 36 acts on and / or regulates the hydraulic oil flow coming from said lifting cylinder (FIG. .1) and into it, respectively.

The design of the second control valve 15 follows the same basic principles. In the hole between said pump compartment 33 and said return compartment 34, there is a second flow restrictor, which together with the second valve seat 56 forms the main valve of said control valve 15 in said housing element 30. The said main valve of said control valve 15 functions as a check valve and at the same time functions proportional control valve, which will be explained later.

Said flow restrictor 55 is actuated by a return spring 57. By said return spring 57, said main valve remains locked until the pressure P _n in said pump compartment 33 exceeds the pressure P _z in said return compartment 34. This occurs, for example, when said pump (FIG. 1) does not work.

At the same time, said flow restrictor 55 is influenced by adjusting devices driven by the selection of said valve 100. Unlike the distribution valve 5 described above, said proportional magnet 103 acts on said flow restrictor 55 in said distribution valve 15 without an indirect counter-piston involvement. Said flow restrictor 55 is also actuated by said auxiliary valve 101. This is as follows.

Mentioned proportional magnet 103 in a known manner through the solenoid plunger 61 moves the auxiliary piston 63, compressing the auxiliary adjusting spring 62. As a result of the movement of the said auxiliary piston 63 in the pressure compartment 64 in the control system, the pressure P _{y is created} . Said pressure P _y depends on the movement of said auxiliary piston 63 and is thereby also determined by said auxiliary adjustment spring 62. Since said auxiliary valve 101 determines the pressure P _n in said pump compartment 33 by means of an additional connecting channel 65, and also by means of the aforementioned connecting channel 46 determines the prevailing pressure in the above-mentioned return compartment 34, to set the desired pressure P _y in the control system does not require any adjusting devices. Since said connecting channel 65 is in a different plane, it is shown with a dashed line to illustrate how it allows a connection to be established between the auxiliary valve 101 and the pump compartment 33, bypassing said return compartment 34.

Said auxiliary valve 101 regulates the said pressure P _y , which is functionally dependent on the pressures in the pump compartment 33 of the cylinder and the return compartment 34, as well as on the rise of the auxiliary valve 63, which is also determined by the choice of said auxiliary valve 101. Due to the pressure P _y the impact on the piston 68, displaced in the compartment 67 adjustment. Said piston 68 is supported by said housing element 30 through an adjustment spring 69 of the main valve. The movement of said piston 68 by means of a pusher 70 is communicated to said flow restrictor 55. Thus, said main valve adjusting spring 69, on the one hand, acts as a reset spring of said piston 68, and on the other hand, as an adjusting spring of said main valve of said control valve 15. In accordance with the invention, this is also not required any adjusting devices.

This is shown more clearly in FIG. 3. In particular, a state is shown when said pump 10 is operating, whereby under the influence of an increased pressure P _n, said flow restrictor 55 presses the return spring 57 and thereby rises from the valve seat 56. Since proportional magnate 103 is selected, said piston 68 is biased to the left under the influence of increased pressure P _y , i.e. in the direction of said flow restrictor 55. By means of said pusher 70, the movement of said piston 68 is communicated to said flow restrictor 55.

As soon as the mentioned pump 10 starts to work, the pressure P _n rises. Said main valve of said distribution valve 15 immediately opens due to the fact that said flow restrictor 55 presses on the return spring 57. The hydraulic oil supplied by said pump 10 from said pump compartment 33 enters into said return compartment 34, and from there through said return line 14 (FIG. 1) into said tank 11. It should be further noted that said flow restrictor 35 of said distribution valve 5 cannot press on said return spring 37 because, due to the relatively high pressure P _z created by the load of said elevator car 1, said main valve of said first distribution valve 5 under any circumstances remains locked due to the positive pressure difference P _z - P _p .

In order to initiate the upward movement of said elevator car 1, said control valve 15 activates a proportional control valve, as indicated above. This is done by selecting said proportional magnet 103 through a control line 26.

As further shown in FIG. 3, under the influence of the increased pressure P _{p, the} flow restrictor 35 of said main valve of said control valve 5 also pressed against the return spring 37. This occurs as soon as said pressure P _{n is} so much higher than said pressure P _z that the compression force of the spring of said return spring 37 will also be overcome. As shown in figure 3, upon receipt of oil for the hydraulic system through line 4 of the cylinder in said lifting 3 cylinder, the latter moves up the aforementioned car 1. It should be noted that said main valve of said first distribution valve 5 opens without selecting said proportional magnet 102, i.e. without interaction only with the aforementioned auxiliary valve 100, which is explained positively by the pressure difference P _p - P _z . The upward movement of said elevator car 1 is thus ensured only by selecting said proportional magnet 103, and said main valve of said first distribution valve 5 only performs the function of a check valve.

Similarly to said control valve 5, said control valve 15 also consists of a counter piston 58 and a pusher 59. In contrast to said control valve 5, wherein said pusher 39 is attached to said counter piston 38 and said flow restrictor 35 is made as a separate element, said counter piston 58, the pusher 59 and the flow restrictor 55 in said control valve 15 are integrally formed. These differences are clearly shown in FIGS. 2 and 3. Said counter piston is located in a recess 60 in said first housing element 30 when said control valve 15 is locked. The diameter of said recess 60 may undoubtedly exceed the diameter of said counter piston 58. In this case, said counter piston 58 does not affect, in the sense of force, said main valve of said distribution valve 15 formed by a flow restrictor 55 and a valve seat 56.

As for the functions of counter-piston 38 and 58, they are different in meaning. The pressure in said pump compartment 33 of said counter-piston 38 and 58 acts similarly on said flow restrictors 35 and 55. If the diameters of the counter piston 38 and 58 are predominantly identical to the diameters of the flow restrictors 35 and 55, a balance of forces occurs. In said first control valve 5, in which the flow restriction 35, on the one hand, and the counter piston 38 with the pusher 39, on the other hand, are made as separate elements, the same force acts on said counter piston 38 and said flow restrictor 35, created by pressure P _p . Thus, said force, which must be created by said auxiliary valve 94, in order to move said piston 48 and said pusher 60 towards counter piston 38 and said flow restrictor 35, does not change due to the difference in forces. In said control valve 15, said counter-piston 58 is rigidly connected to said flow restrictor 55, since in this case said counter-piston 58 is located on the side of said main valve and is not facing towards said auxiliary valve 101, due to which no transmission occurs through said counter-piston 58 efforts. Since the diameter of said recess 60 is noticeably greater than the diameter of said counter-piston 58, the pressure P _p in said counter-piston 58 is directed in all directions, i.e. does not create a reaction force to said flow restrictor 55.

Figure 4 shows the position of the said block 28 of the control valves when moving down the aforementioned cabin 1 (Fig. 1) of the elevator. The pump 10 (figure 1) does not work. Accordingly, the pressure level P _{p is} low. Before the downward movement of said elevator car 1 starts, due to the fact that the pressure P _z in said cylinder compartment 32 is noticeably higher than the pressure P _p in said pump compartment, said main valve of said distribution valve 5 formed by a flow restrictor 35 and a valve seat 36, locked up. To initiate a downward movement of said elevator car 1, said proportional magnet 102 is selected which, through the solenoid plunger 41, acts on said auxiliary valve 100, which generates pressure P _x in said adjustment compartment 47. The magnitude of said pressure P _z is determined by the selection of said proportional magnet 102 and said auxiliary adjusting spring 42, as well as the pressure P _z in said cylinder compartment 32 and the pressure in said return compartment 34. As said proportional magnet 102 is selected, said pressure P _x in said pressure compartment 44 in the control system rises, whereby said piston 48 moves, counteracting the force of said main valve adjustment spring 49, in the direction of said counter piston 38. Said pusher 50 transfers this movement said counter-piston 38, which, through said pusher 39, is transmitted to said flow restrictor 35. Thereby, said main valve of said distribution valve is torn off.

As a result of this, the pressure P _r increases in said pump compartment 33. Due to this, said flow restrictor 55 is pressed against said return spring 57, after which said flow restrictor 55 rises from said valve seat 56. After that, the hydraulic oil can be supplied through the main valve formed by the said flow restrictor 55 and said seat 56, and through the said return compartment 34 along said line 14 (Fig. 1) to said tank 11. For completeness, it should be noted that a part of said hydraulic oil may also flow back to said tank 11 from said pump compartment 33 via said pump line 8 (FIG. 1) through said pump 10, since in such a pump x typically the losses occur as a result of leakage. How much of the flow will flow through said pump 10 depends on the type of construction of said pump 10 and the stiffness of said return spring 57. Depending on the type of construction of said pump 10, it is likely that said pump 10 is driven by an oil flow for a hydraulic system, although it is not driven by an electric motor 12. For the sake of completeness, it should also be noted that through said auxiliary valve 100 also receives an additional part of the stream.

Thus, during the downward movement formed by the flow restrictor 55 and valve seat 56, said main valve of said control valve 15 acts as a check valve, which opens only under the influence of said pump pressure P _p . Thereby, no selection of said proportional magnet 103 occurs, and said auxiliary valve 101 is also not used.

Thus, in order to control the up and down movement of said elevator car 1 (FIG. 1) in accordance with the present invention, only the two distribution valves 5 and 15, respectively, which combine the functions of a non-return valve and a directional control valve with proportional control, are required. At the same time, said non-return valve functions of said distribution valves 5 and 15 meet the safety requirements of EN standards. Thus, said control valve 5 acts as a safety valve, and said control valve 15 makes an additional pump pressure control valve unnecessary. Thus, in accordance with the present invention, said control valve block 28 is distinguished by its particular simplicity of construction and low production cost. According to a preferred embodiment of the invention, the flow restrictors 35 and 55 are identical, which gives the advantage of production costs since various flow restrictors are required to be manufactured.

Advantageously, the surfaces of said counter-piston 38 and 58 facing the said flow restrictors 35 and 55, respectively, have not a flat shape, but a truncated cone shape. 5 shows a locking member 55 with a counter piston 58 and said pusher connecting them. The surface facing the said locking element 55 has the shape of a truncated cone 80. Preferably, the surface of the truncated cone 80 forms an angle α of about 15 to 25 degrees with a surface perpendicular to the longitudinal axis. Due to this, dynamic loads arising at a high intensity of the flow entering through the main valve of said distribution valve 15 do not adversely affect said auxiliary valve 101.

It is also preferable if the shape and dimensions of said counter piston 58 of said control valve 15 are similar to the shape and dimensions of said counter piston 38 of said control valve 5. If said counter pistons 38 and 58 are identical, the number of different components to be manufactured and stored will be reduced, and the production volume the party will double, which will positively affect production costs. It is also important for on-site maintenance. FIG. 6 shows a counter piston 58, the shape and dimensions of which correspond to the shape and dimensions of said counter piston 38 (FIG. 4). In this case, the aforementioned angle α is also formed.

7 also shows a counter piston, which can be used as a counter piston 38 of said control valve 5 and as a counter piston 58 of said control valve 15, while an angle α is also formed.

The dimensions of said recess 60 are selected taking into account the dimensions of said counter piston 58, in other words, if said counter piston 68 is made in accordance with FIG. 5, the depth of said recess 60 is small. If, however, the dimensions of said counter piston 58 correspond to those shown in FIG. 6, the depth of said recess 60 increases accordingly, whereby said counter piston 68 is placed in said recess 60 when the main valve of said second control valve 15 is locked.

On Fig-11 shows the elements of the mentioned flow restrictors 35, 55, in particular, various embodiments. A cylinder 91 is placed on the base 90, the housing surface of which is indicated by 92. In said cylinder 91 there are openings 93 through which said hydraulic oil can pass. Preferably, around the circumference of said cylinder 91, for example, six openings 93 can be evenly spaced. The said openings 93 may have a different shape. According to the embodiment shown in FIG. 8, said openings 93 are V-shaped in the space following said base 90, and in the space following it, they have a constant width. As a result, as the rise of the aforementioned flow restrictor 35, 55 increases, the useful cross-sectional area of the hydraulic oil hole first increases exponentially, and then increases linearly with a further increase in lift. According to the embodiment shown in FIG. 9, the openings 93 are not V-shaped, but bell-shaped in the space following the base. As a result, the useful cross-sectional area of the oil hole of the hydraulic system changes nonlinearly. When the mentioned control valves 5 and 15 are locked, respectively, in the case of operation in the opening direction, the useful sectional area of the hydraulic oil hole first increases slightly, then continues to increase as the lift increases, and with a further increase in lift it increases to a lesser extent. Subsequently, she again becomes permanent.

Figure 10 shows an example whereby said openings 93 change in steps. On the first surface of the lift, the hole 93 has a V-shape, sharply turning into a rectangular one. This means that the useful cross-sectional area of the oil hole for the hydraulic system first increases slightly, then sharply reaches its maximum value, after which it ceases to depend on further rise.

Figure 11 shows a further example, according to which the aforementioned holes 93 change only stepwise. On the first surface of the lift, said openings 93 have a small diameter, and then increase sharply and change their shape to a rectangular one. This means that the useful cross-sectional area of the oil hole for the hydraulic system first has one value, and then changes sharply, reaching the maximum value, after which it ceases to depend on further rise.

Thus, due to the shape of said flow restrictors 35, 55, the throughput of said control valves 5 and 15 can be adapted over a wide range to the respective elevator systems and control methods. The above examples provide an idea of the possibilities offered. By imparting to said restrictors 35 and 55 flows of various shapes, said control valves 5 and 15 can be adapted to various tasks and systems. It is known from the technology to use structures of various kinds and sizes for various purposes. Thus, in the present invention due to minor modifications of one block 28 of the control valves, both small and large elevator systems are controlled.

Another embodiment of the preferred embodiment is that limitation of lift is provided. This limitation can be achieved mainly due to the fact that the possible trajectory of movement of the said pistons 48 or 68, respectively, inside the said compartments 47 or 67 of the regulation is limited. 12 and 13 show corresponding modifications.

12 shows the element illustrated in FIGS. 2-4, in particular said adjustment compartment 47 or 67, respectively, with pistons 48 or 68 moving inside them, respectively. There are several annular grooves 95 on the cylindrical inner wall of said adjustment compartment 47 or 67, respectively. Locking rings 96 are inserted into said annular grooves 95. Depending on the limitation of the lifting, the retaining ring 96 is inserted into one of said annular grooves 95. As a result, the degree of lifting is limited piston 48 or 68, respectively. In exact accordance with it, the degree of lift of said flow restrictor 35 or 55 is also limited, respectively, of said control valves 5 or 15 (FIGS. 2-4). In this way, in the assembly process of said distribution valve block 28, it can be determined what its dimensions should be at maximum nominal flow. Thus, there is no need for the design of the blocks 28 of the distribution valves of various sizes.

13 shows a preferred embodiment of a lift restriction. In this case, annular grooves 95 are not required (Fig. 12), the manufacture of which is associated with technological problems. Instead, a snap ring 97 is respectively inserted into said adjustment compartment 47 or 67. Its outer diameter is slightly smaller than the diameter of said adjustment compartment 47 or 67, respectively. In this case, the length of said cylindrical intermediate ring defines a lifting restriction. In contrast to the variant shown in FIG. 12, according to which the possible lifting restrictions are equal to, for example, 5, 8, 11 and 14 mm, depending on the position of said individual grooves 95, in this case it is possible to set an arbitrary lifting restriction.

Fig. 14 shows an element of said pistons 48, 68. A groove 98 is inserted in their outer circumference, into which an elastic ring seal 99 is inserted. Said seal 99 substantially fills the gap between the cylindrical outer surface of said pistons 48, 68 and the inner wall of said compartment 47, 67 adjustment (figure 2). Said seal 99 advantageously fulfills the task of reducing leakage, since owing to it, oil leakage for the hydraulic system from said compartment 47, 67 towards said main valve of said control valves 5, 15 is substantially reduced.

On Fig shows the surface of the housing of the flow restrictor 35 (figure 2). The openings 93 previously mentioned with reference to FIGS. 8-11, having different shapes but the same size corresponding to the flow restrictor 35, in this case have different sizes. Said hole 93 according to FIG. 11 starts at a distance d from said base 90 (FIGS. 8-11), an additional hole 104 at a distance d ’, and another additional hole 105 at a distance d’ ’. The distance d is the smallest and equal to, for example, 1 mm. Since the individual openings 93 have different sizes, mainly due to the choice of the individual distances d, d ’, d’ ’, etc., the flow parameters depending on the valve lift mentioned above can be arbitrarily adjusted in order to adapt them to the respective needs.

16 and 17 show possible additional elements of the openings 93. FIG. 16 shows a hole 93, the beginning of which 106, like the hole shown in FIG. 15, is at a predetermined distance from said base 90. The depth of such a hole, as well as its width is preferably calculated according to the dimensioning formula, according to which the usable area A of said opening 93 depends on the distance y from said beginning 106. According to a particularly preferred dimensioning formula, the area A is proportional to the distance y, ennomu in 2.5 degree, i.e. calculated by the following formula:

A = k · y ^2.5

in this case, k is the coefficient of proportionality.

FIG. 17 shows a cross-sectional view of FIG. 16 with a distance from said beginning 104. Unlike the embodiment shown in FIG. 15, the beginning 106 of all holes 93 are at the same distance from said base 90, however, this embodiment may be combined with the embodiment according to Fig.11. This is shown in FIG. 17, where one of the holes is shown by the dashed line to be deeper, since its beginning 106 is at a shorter distance from said base 90.

On Fig shows a particularly preferred shape of the boundaries of the holes 93. In the region of the beginning of the aforementioned holes 93, its radius is, for example, 1 mm Curved boundaries correspond to an arc of 180 °. By changing said boundaries, certain flow parameters can be provided.

The specific dimensions of the above-mentioned openings 93 described above are intended to provide a sufficiently wide range of pressure adjustment for any flow parameters.

Said control valve block 28 according to the present invention has been described with reference to FIG. The mentioned sensors 18 and 28, necessary in such devices, were not shown in the subsequent drawings, since they are already known from the prior art. The same applies to the temperature sensor.

However, the control valve unit 28 according to the present invention is designed to be used not only in the system shown in FIG. 1 in the operation mode described with reference to FIG. 1. Thus, the control valve block 28 according to the present invention can also be freely used in other design modifications, for example, in the case where the speed of the pump 10 is regulated, as a result of which the control principle of the said control valve block 28 also changes.

Claims (17)

1. The block (28) of the elevator control valves with a hydraulic actuator, including the control valves (5, 15) and auxiliary valves (100, 101), with which they regulate the oil flow for the hydraulic system from the tank (11) to the lift a cylinder (3) driving the elevator car (1), and / or from said lifting cylinder (3) to said tank (11), in which the upward movement of said elevator car (1) is provided due to the fact that said oil for hydraulic system from said tank (11) is fed into said a lifting cylinder (3) through said distribution valve block (28) by means of a pump (10) driven by an electric motor (12), and the downward movement of said elevator car (1) is provided due to the fact that said hydraulic oil is supplied through said block (28) of distribution valves to said tank (11), in which the downward movement of said elevator car (1) is controlled by one single controlled distribution valve (5), acting as a non-return valve and also as a directional control valve control, and the upward movement of said elevator car (1) is controlled by one single controllable control valve (15), acting as a check valve, as well as a proportional control valve, characterized in that the force of said auxiliary valve (100) of said control valve (5 ), which controls the downward movement, transfers the piston (48), using the pusher (50) presses the adjustment spring (49) of the main valve to the counter-piston (38), which, by means of the pusher (39) attached to it, moves There is a flow restrictor (35), and the force of the aforementioned auxiliary valve (101) of the above control valve (15) controlling the upward movement is transmitted by the piston (68), by means of a pusher (70) pressing the control valve spring (69) of the main valve to the restrictor (55) ) flow rigidly attached to the counter-piston (58) using a pusher (59). 2. Block 28 of the control valves according to claim 1, characterized in that each of the said control valves (5, 15) has one single flow restrictor (35, 55) that can move relative to the seat (36, 56). 3. Block (28) of the distribution valves according to claim 2, characterized in that the return flow spring (37; 57) acts on the said flow restrictor (35; 55), as well as an auxiliary valve (100, 101), actuated by electrically selectable magnet (102, 103) with proportional control. 4. Block (28) of the distribution valves according to claim 3, characterized in that in the upward movement control process, the return spring (57) and the auxiliary valve (101) of said distribution valve (15) equally act on the flow restrictor (55) in the direction locking the valve. 5. Block (28) of the distribution valves according to claim 3, characterized in that in the process of controlling the upward movement, the return spring (57) acts on the flow restrictor (35) in the locking direction, while the auxiliary valve (100) in the unlocking direction. 6. Block (28) of the control valves according to claims 4 and 5, characterized in that said flow restrictor (35) of said control valve (5) downstream and said flow restrictor (55) of said control valve (15), controlling the upward movement, have the same shape and size. 7. Block (28) of the control valves according to claim 6, characterized in that the diameter of said counter-piston (38) is equal to the diameter of said flow restrictor (35). 8. Block (28) of control valves according to claim 6, characterized in that the diameter of said counter-piston (58) is equal to the diameter of said flow restrictor (55). 9. Block (28) of the distribution valves according to claim 7 or 8, characterized in that a groove (98) passes through the outer circumference of the said piston (48; 68), in which an elastic seal (99) is placed. 10. Block (28) of control valves according to claim 7 or 8, characterized in that the surface of said counter-piston (38, 58) facing the said flow restrictor (35, 55) has the shape of a truncated cone. 11. Block (28) of control valves according to claim 10, characterized in that said flow restrictors (34; 55) are formed by a base (90) and an adjacent cylinder (91), in the surface (92) of which there are openings (93) ) 12. Block (28) of the distribution valves according to claim 11, characterized in that at least a portion of said openings (93) is V-shaped. 14. Block (28) of the distribution valves according to claim 11, characterized in that at least a portion of said openings (93) has a bell-shaped shape. 15. The block (28) of the distribution valves according to claim 11, characterized in that the said openings (93) change stepwise. 16. The control valve block (28) according to one of claims 7 and / or 8-15, characterized in that there is a means (95, 96, 97) by which the lifting of said pistons (48; 68) is limited. 17. The control valve block (28) according to claim 16, characterized in that the trajectory is limited by a retaining ring (96) inserted into one of several annular grooves (95) passing along the cylindrical inner wall of the adjustment compartments (47; 67). 18. The control valve block (28) according to claim 16, characterized in that a cylindrical retaining ring (97) can be inserted into said adjustment compartment (47; 67), the outer diameter of which is slightly inferior to the diameter of said adjustment compartment (47; 67) , and the length of which determines the limitation of the rise.

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