Radiator thermostat

Abstract

A radiator thermostat (1) to be fitted onto a radiator valve (4) is provided. The radiator thermostat (1) has a transmission element (5, 105, 205) that transmits a compressive force to the valve pin (8) of the radiator valve. An electric motor (12) is provided to drive the transmission element (5, 105, 205). The transmission element (5, 105, 205) is preloaded with a counter force (F2) that acts in opposition to the valve force (F1) using a spring (18; 20; 32). Thus, when moving the transmission element (5, 105, 205), the motor (12) has only to overcome the differential force (df).

Claims

1. A radiator thermostat to be fitted onto a radiator valve (4) comprising a transmission element (5, 105, 205) for transmitting a compressive force to the radiator valve (4), an electric motor (12) for driving the transmission element (5, 105, 205), a control for the electric motor (12), and a power supply comprising a thermoelectric energy converter (25) to convert thermal energy into electrical energy and an energy storage unit (27) to store the electrical energy, wherein the transmission element (5, 105, 205) is preloaded in a direction of the valve, and the control is configured to perform a regulating movement to close the radiator valve only when sufficient energy remains in the storage unit to later re-open the valve again.

2. The radiator thermostat according to claim 1, wherein the transmission element (5, 105, 205) is preloaded in the direction of the valve (19) using a spring (18; 20).

3. The radiator thermostat according to claim 1, wherein the transmission element (5) interacts with an outer ring (31) of an antifriction bearing (30) or with an outside circumference of a bearing bush of a sliding bearing, an inner ring (29) of the antifriction bearing (30) or a bearing surface of the sliding bearing is disposed at an outside circumference of an eccentric disk (14).

4. The radiator thermostat according to claim 3, wherein the outer ring (31) of the antifriction bearing (30) or the outside circumference of the bearing bush of the sliding bearing receives a force in the direction of the transmission element (5) via at least one spring (32).

5. The radiator thermostat according to claim 4, wherein the at least one spring (32) is formed as a substantially U-shaped tension spring having legs (33) that are folded more than two times and having a base (34) that is led around the outer ring (31) of the antifriction bearing (30) or around the outside circumference of the sliding bearing bush and rests against a side facing away from the transmission element (5).

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The drawings show:

(2) FIG. 1A a cross-section through a radiator valve,

(3) FIG. 1B a cross-section through a radiator thermostat having an eccentric and two ball bearings to transmit the force,

(4) FIG. 2 a longitudinal section through the radiator thermostat of FIG. 1b,

(5) FIG. 3 a cross-section through a radiator thermostat having an alternative arrangement of the eccentric and the two ball bearings,

(6) FIG. 4 a longitudinal section through the radiator thermostat of FIG. 3,

(7) FIG. 5 a cross-section through a radiator thermostat having a toothed rack on the transmission element and a toothed wheel on the motor shaft,

(8) FIG. 6 an oblique view of the radiator thermostat of FIG. 5,

(9) FIG. 7 a cross-section through a radiator thermostat having a jointed connecting rod that connects the motor shaft to the transmission element,

(10) FIG. 8 an oblique view of the radiator thermostat of FIG. 5,

(11) FIG. 9 a radiator thermostat according to FIG. 1b having a thermal energy converter as the source of energy,

(12) FIG. 10 a cross-sectional view of a further embodiment of a radiator thermostat according to the invention having a thermal energy converter,

(13) FIG. 11 a view from above of the radiator thermostat of FIG. 10,

(14) FIG. 12 an exploded view of the radiator thermostat of FIG. 10,

(15) FIG. 13 the tension spring of the radiator thermostat of FIG. 10, and

(16) FIG. 14 the heat sink of the radiator thermostat of FIG. 10.

DETAILED DESCRIPTION FOR THE PREFERRED EMBODIMENTS

(17) FIGS. 1B and 2 show a first possible embodiment of a radiator thermostat according to the invention that is indicated in its entirety by 1. The radiator thermostat 1 has a housing 2 having a flange 3 with which the housing 2 can be attached to a radiator valve 4. The radiator valve 4 in FIG. 1A has a valve seat 4 and a valve disk 4 that fits into the valve seat 4 such that the through flow can be closed. Through a linear movement of the valve disk 4, the amount of through flow can be regulated. The valve disk 4 is connected to a linearly moveable guide unit in which a spring pushes the guide unit, and thus the valve disk 4, away from the valve seat 4. The valve is thus open in the neutral position. In the example, the housing 2 is formed in two parts, although the type of housing 2 does not basically affect the function.

(18) The radiator thermostat 1 has a transmission element 5 that has a cylindrical transmission pin 6 at one end. The transmission pin 6 is supported in the housing 2 so as to be linearly moveable and projects from the free end 7 into the flange 3, where it rests against the valve pin 8.

(19) At the inside end 9 of the transmission element 5, an axle 10 is disposed onto which the inner ring of a first ball bearing 11 is firmly fitted.

(20) The radiator thermostat 1 furthermore has an electric motor 12 on whose shaft 13 an eccentric disk 14 is fixed. At the circumference of the eccentric disk 14, the inner ring of a second ball bearing 15 is seated. The two ball bearings are disposed with respect to one another such that the two outer rings roll against one another and that the rotational axes of the ball bearings and of the motor, except for a sideways movement caused by the eccentricity of the eccentric, lie in one line with the longitudinal axis 16 of the transmission pin 6.

(21) On the side of the second ball bearing 15 located opposite the first ball bearing 11, the outer ring of the second ball bearing 15 rests against a counter bearing 17, the contact point lying approximately on the longitudinal axis 16 of the transmission pin 6. The counter bearing 17 is approximately shaped like a beam that extends at a right angle to the longitudinal axis 16. At each of the two lateral ends of the beam 17, a tension spring 18 is disposed that is tensioned on the housing 2 in the direction of the valve flange 3 and applies a force to the counter bearing 17 in the direction of the valve 19.

(22) When the motor 12 is switched on, the eccentric disk 14 rotates with the shaft 13 of the motor 12. Because it is connected to the first ball bearing 11, the transmission pin 6 consequently makes a linear movement in a longitudinal direction. A valve pin 8 connected to the transmission pin 6 is thereby moved, so that the valve 4 opens or closes, depending on the rotational position of the eccentric disk 14.

(23) Two forces act on the transmission element 5 at all times. One is the compressive force F1 of the radiator valve 4 with which the valve pin 8 is tensioned. The spring resistance F2 with which the counter bearing 17 is preloaded acts in opposition to this force F1. Ideally, the two forces have approximately the same strength about the chosen operating point. The opening in the valve 4 is determined by the rotational position of the eccentric 14.

(24) In order to move the transmission pin 6, the electric motor 12 need now only provide the differential force dF=F1F2 of the two outer forces in each position. This differential force dF increases the more the valve closes. On the one hand, the preload force of the springs 18 decreases in the process, and, on the other hand, an ever increasing counter force has to be overcome because of the spring in the radiator valve. Since this differential force dF is less than it would be without the counter force F2, the motor 12 requires less force and thus less electrical energy.

(25) Moreover, since the rotational movement of the motor is converted into a linear movement of the transmission pin using the eccentric disk 14 and the ball bearings 11, 15, it is practically only rolling friction that occurs here that requires very little extra energy.

(26) Since the motor 12 requires only low torque, a small, economical motor can be used which, moreover, does not need strong reduction gearing.

(27) Taken as a whole, the electric drive is thus very economical compared to the prior art so that a battery, for example, used for the power supply has a considerably longer useful life.

(28) Instead of using the illustrated ball bearings to convert the rotational movement, other bearings such as needle bearings, roller bearings or other types of anti-friction or sliding bearings could also be used.

(29) In FIGS. 3 and 4, an alternative embodiment of the invention is shown that is substantially based on the embodiment of FIGS. 1 and 2. Here, however, the second ball bearing 15 is disposed on the counter bearing 17 and the eccentric disk 14 is disposed between the two ball bearings 11 and 15 such that it rolls on the outer rings of the two ball bearings. The rotational axes of the ball bearings and of the motor here again lie on the longitudinal axis 16 of the transmission pin 6. Here, the movement of the transmission pin 6 acts in accordance with the same principle as in the embodiment of FIGS. 1 and 2.

(30) A fundamentally different embodiment is shown in FIGS. 5 and 6. Here, the transmission element 105 is made somewhat longer and, at its inside end 9, is tensioned by a compression spring 20 in the direction of the valve 19. In the example, the compression spring 20 takes the form of a coil spring that is held in a recess 21 in the housing 2.

(31) At least a section of the transmission element 105 has a toothed rack 22 that interacts with a toothed wheel 23 on the motor shaft 13. The mechanics in this embodiment are somewhat less complicated, but there is greater overall frictional loss compared to the embodiments having an eccentric 14.

(32) The embodiment of FIGS. 7 and 8 has a similar design to the embodiment of FIGS. 5 and 6. Here, instead of using the toothed rack 22 to transmit the movement, a jointed connecting rod 24 is fixed to the transmission element 205 and to the motor shaft 13. The rotation of the motor shaft 13 is thereby converted into a linear movement of the transmission pin 6.

(33) An advantageous development on the invention is shown in FIG. 9. This embodiment substantially corresponds to the embodiment of FIGS. 1B and 2. Here, the housing 2 is given a somewhat different shape, although this in no way influences the function.

(34) As its power supply, however, this embodiment has a thermal energy converter 25 that converts thermal energy into electrical energy. To this end, the flange 3 used for mounting on the radiator valve 4 is preferably made of metal that allows the best possible conduction of heat from the radiator. The energy converter 25 is directly connected on one side to the flange 3 and, on the other side, to the heat sink 26. Since the energy converter 25 needs a flow of heat, the heat should flow through the energy converter 25 with the least possible obstruction. Moreover, the greatest possible difference in temperature is advantageous, which is why the heat sink 26 is made as large as possible.

(35) The electrical energy generated in the energy converter is preferably stored in an energy storage unit 27, such as a rechargeable battery or a capacitor.

(36) Since there is permanent heat in the radiator valve during heating, electrical energy can be constantly collected. Depending on the design of the energy converter 25, enough energy can be collected within a few minutes to enable the valve 4, for example, to be fully opened or closed. For short regulating distances, less time is accordingly required. For this purpose, a very small, low-cost energy converter is sufficient since, thanks to the economical drive according to the invention, only a small amount of energy is consumed.

(37) This kind of radiator thermostat no longer needs an external source of energy and can thus be operated fully self-sufficiently and maintenance-free. Troublesome and expensive battery changes are no longer necessary.

(38) Here, it has proven particularly advantageous to only permit a regulating movement, particularly to close the radiator valve, when sufficient energy remains in the storage unit to re-open the valve once more. In the open position, the thermal energy converter is again operative.

(39) Crucial to the invention is that the transmission element is preloaded with a counter force F2 acting in opposition to the force F1 of the radiator valve and that the electric motor need then only provide the differential force dF in order to operate the valve.

(40) A further advantageous embodiment of the invention is shown in FIG. 10 whose construction is substantially the same as the embodiment of FIG. 9.

(41) In this embodiment, the eccentric disk 14 is disposed on a shaft 28 that is driven by the electric motor 12. The inner ring 29 of an antifriction bearing 30 is disposed at the outside circumference of the eccentric disk 14. The antifriction bearing 30 may, for example, be a ball or needle bearing. The outer ring 31 of the antifriction bearing 30 acts directly on the transmission element 5, which, in this embodiment, only has a transmission pin 6. As it is shown in the example, the pin can exhibit a head in order to enlarge the contact area with the outer ring 30 of the antifriction bearing 30. The antifriction bearing 30 is moreover preloaded in the direction of the transmission element 5 by means of a spring. This preload can be effected, for example, using a compression or tension spring.

(42) In the example, the preload is effected using a one-piece, substantially U-shaped tension spring 32 whose legs 33 are attached to the side of the transmission element 5 while the base 34 is led around the outer ring 31 of the antifriction bearing 30 and essentially engages directly opposite the transmission element 5 at the outer ring 31 (FIG. 11). The legs 33 are folded several times which goes to produce the spring effect. (FIGS. 12 and 13)

(43) Instead of this one-piece spring 32, one or two differently shaped tension or compression springs may also act, for example, on a fixed bar that rests on the outer ring 31 of the antifriction bearing 30.

(44) It is preferable if the eccentric disk 14 is not disposed directly on the motor shaft but rather on an output drive gear 35 of a reduction gear unit 36. This allows the motor 12 to be operated at higher rotational speed and lower torque.

(45) Instead of the antifriction bearing 30, the transmission element may also interact with the bearing bush of a sliding bearing. The eccentric disk then acts as a shaft that is supported in the sliding bearing surface.

(46) For its energy supply, this embodiment also has a thermoelectric energy converter 25 taking the form of a thermoelectric generator (TEG). This TEG 25 is seated between the flange 3 and a heat sink 26.

(47) For it functioning, it is important that as much heat as possible flows through the TEG 25. The thermal resistance between the flange 3, the TEG 25 and the heat sink 26 should thus be as low as possible. Consequently, in this embodiment, the heat sink 26 is subjected to a further compression spring 37 that is seated between the housing wall 38 and the heat sink 26 and presses the heat sink 26 against the TEG 25.

(48) In addition, a contact medium 40 is disposed between the TEG 25, the flange 3 and the heat sink 26, the contact medium 40 minimizing thermal resistance. This contact medium 40 may, for example, be a thermal paste. In the example the contact medium 40 is Indium.

(49) Furthermore, it is advantageous if the difference in temperature between the flange 3 and the heat sink 26 is as large as possible. It is thus necessary for the heat conducted to the heat sink 26 to be led away from the housing 2 as effectively as possible. Hence, all the components in the housing 2 are disposed such that within the housing 2 there is a path open from the bottom to the top in which air can rise. For this purpose, appropriate ventilation vents 39 are provided in the housing 2.

(50) This chimney effect causes a continuous flow of air through the housing 2, particularly past the heat sink 26. This allows the heat at the heat sink 26 to be continuously transported upwards out of the housing 2, which goes to improve the efficiency of the TEG 25.

(51) The heat sink 26 preferably has a plurality of cooling fins 41 that are at least partially free-standing, so that the current of air 43 created by the chimney effect flows through the slots 42 between the cooling fins 41 (FIG. 14) thus ensuring a more effective dissipation of heat. In addition, the heat sink 26 preferably has a projection acting as a contact point 43 for the TEG 25, so that the flow of heat is concentrated through the TEG 25. The projection furthermore acts as a spacer between the heat reservoir (heating circuit) and the cooling reservoir (cooling element), so that they are thermally insulated from one another and the greatest possible temperature gradient occurs along the thermo element. To intensify this effect, insulating material may additionally be placed between the warm side and the heat sink 26.

(52) Alongside the TEG 25, the radiator thermostat 1 according to the invention may have an interface for externally charging an energy storage unit 27 that may, for example, be disposed on a circuit board 44. In the example, a battery is shown as the energy storage unit 27 although one or more capacitors or a combination of the two kinds of energy storage units may be used. Moreover, the radiator thermostat 1 may be configured via this interface, which is made possible by using, for example, USB, IEEE 1394 (FireWire), Thunderbolt or similar interfaces. Furthermore, the radiator thermostat 1 may have a wireless interface (e.g. ZigBee, Bluetooth, Bluetooth low energy, WLAN, Z-Wave) that can send measured data to a receiver and can receive control commands from a control device. This wireless interface, such as ZigBee or Z-Wave, is preferably optimized to low energy consumption. For this purpose it is activated, for example, at intervals for only a short period of time.

(53) The radiator thermostat 1 monitors the surrounding temperature, the initial flow temperature in the radiator and the valve position so that it can be used directly for determining consumption. It is no longer necessary to determine consumption separately using evaporation tubes or suchlike. Determining consumption using the radiator thermostat 1 is much more accurate thanks to the precise sensor system.

(54) Alongside the illustrated embodiments, there are a large number of other means of applying the preload to the transmission element, which is why the invention is in no way limited to these embodiments. In particular, by giving the mechanical parts a different design and thus a different construction, a compression spring could be substituted for a tension spring and vice versa.

(55) To program and regulate the radiator thermostat, a variety of control methods can be provided. For one thing, the radiator thermostat can be provided with a display, such as an LC display, to display the operating status and the temperature. Within the control, provision can also be made for different operating statuses to be predetermined in different periods of time. To this end, the radiator thermostat contains a date/timer unit. The parameters are entered either using key functions that are realized on the radiator thermostat or using a remote control. The remote control can have a display as an alternative or in addition to the radiator thermostat.

(56) All illustrated and non-illustrated embodiments can moreover be provided with at least one energy converter as the only or as an extra source of energy, thus allowing self-sufficient operation. The invention is not thereby limited to thermal energy converters.

IDENTIFICATION REFERENCE LIST

(57) 1 Radiator thermostat 2 Housing 3 Flange 4 Radiator valve 4 Valve seat 4 Valve disk 5 Transmission element 6 Transmission pin 7 Transmission pin free end 8 Valve pin 9 Transmission element inner end 10 First ball bearing axle 11 First ball bearing 12 Electric motor 13 Shaft 14 Eccentric disk 15 Second ball bearing 16 Longitudinal axis 17 Counter bearing 18 Tension spring 19 Direction of the valve 20 Compression spring 21 Recess 22 Toothed rack 23 Toothed wheel 24 Jointed connecting rod 25 Thermal energy converter 26 Heat sink 27 Energy storage unit 28 Shaft 29 Inner ring antifriction bearing 30 Antifriction bearing 31 Outer ring antifriction bearing 32 Tension spring 33 Leg 34 Base 35 Output drive gear 36 Reduction gear unit 38 Housing back wall 39 Ventilation vents 40 Contact medium 41 Cooling fins 42 Slots 43 Contact point 44 Circuit board 45 Energy storage unit 105 Transmission element 205 Transmission element F1 Valve pin force F2 Counter force df Differential force