DE102016205819A1 - Device for cooling a piston of an internal combustion engine - Google Patents

Abstract

The invention relates to a device (1) for controlling a hydraulic fluid supply of an internal combustion engine comprising a supply line (3) extending between an inlet connection P and a supply connection A and a closure element (5a) actuated by means of a hydraulic medium pressure arranged between inlet connection P and supply connection A. is and when a threshold pressure is exceeded, the supply port P connects hydraulically to the supply port A. A first surface (6) of the closure element (5a) faces the supply line (3) and can be brought into spring-loaded engagement with a sealing seat (7). A second surface (9) of the closure element (5a) faces away from the supply line (3) and delimits a pressure space (10). The invention also includes a solenoid valve (26) which controls a hydraulic connection (11) between the supply line (3) and the pressure space (10), the hydraulic connection (11) extending from the first surface (6) to the second surface (9) and wherein the hydraulic connection (11) via an inlet opening (13) opens into the pressure chamber (10), wherein the inlet opening (13) by means of a closing body (14) of the solenoid valve (26) is closable.

Description

The invention relates to a device for controlling a hydraulic fluid supply, in particular for the control of large engine oil volume flows at the same time comparatively small power consumption of a solenoid valve. The invention thus relates, for example, to an apparatus for cooling a piston of an internal combustion engine, comprising a supply line extending between an inlet connection and a supply connection and a closure element actuated by means of a hydraulic medium pressure, which is arranged between the inlet connection and the supply connection and hydraulically connects the inlet connection when a threshold pressure is exceeded connects to the supply port, wherein a first surface of the closure element facing the supply line and spring loaded with a sealing seat can be brought into abutment and wherein a second surface of the closure element facing away from the supply line and a pressure chamber limited, and comprising a solenoid valve, which is a hydraulic connection controls between the supply line and the pressure chamber, wherein the hydraulic connection from the first to the second surface only stretches.

Such a device is for example from the EP 2 778 364 A1 known. Shown is a device for cooling a piston of an internal combustion engine with an inlet connection and an outlet connection, wherein a main line extends between the inlet connection and the outlet connection. Parallel to the main line an auxiliary line is arranged, which thus also extends between the inlet port and the drain port. By means of a first blocking body, the main line can be blocked, wherein a hydraulic connection can be made to a arranged in the auxiliary line blocking chamber via an axially extending through the locking body channel.

With the aid of a second closing body, the auxiliary line can be blocked. As a result, a hydraulic fluid pressure builds up in the lock chamber, whereby the first locking body brought into contact with a sealing seat and the main line is closed. A subsequent release of the auxiliary line thus leads to an opening of the main line.

It is therefore the object of the invention to improve the construction of a device for controlling a hydraulic fluid supply.

The object is achieved by the features of claim 1. A device for controlling a hydraulic fluid supply of the type mentioned is characterized by the fact that the hydraulic connection opens into the pressure chamber via an inlet opening, wherein the inlet opening can be closed by means of a closing body of the solenoid valve ,

The pressure chamber can thus be separated from the hydraulic fluid supply, whereby the second surface is not acted upon by a hydraulic medium pressure. The closure element thus releases the supply line when a defined pressure is exceeded. Advantageously, the opening can be designed to exceed a minimum pressure - and at the same time a failsafe functionality can be realized: A pressure-dependent opening and closing of the closure element is ensured even in the event that the solenoid can not fulfill its functions. In addition, it is ensured that the closure element opens only when a certain minimum pressure of the hydraulic fluid supply is exceeded, so that the pressure build-up is not affected by an early connection with the environment.

The pressure can be defined in particular by the force of a spring, which presses the closure element in the direction of the sealing seat. The spring can be arranged in particular in the pressure chamber, wherein the pressure chamber is limited by a tubular housing and by the closure element on the one hand and by a spring plate on the other. The spring plate can be pressed in particular in the tubular housing, wherein the Einpresstiefe can be influenced to adjust the spring force.

In an advantageous embodiment, the pressure chamber has a drain opening, which can be closed by means of a second closing body of the solenoid valve. The drain opening can be arranged in particular on the spring plate. The drain opening may be for venting in fluid communication with the drain port T, whereby a connection to the environment can be made. In addition, the draining hydraulic fluid can also be supplied to the volume flow which escapes from the supply port A of the device. Advantageously, thus the pressure chamber can be optionally connected to the inlet and the drain. In a further development, a check valve can therefore be arranged in the region of the outlet connection T, for example in conjunction with the second closing body. In this way, a return flow of the hydraulic fluid is avoided in the pressure chamber.

In an advantageous development, the closing body does not close the inlet opening when the drain opening is closed. In this way, a pressure build-up in the pressure chamber is effected, so that the on the closure element acting hydraulic fluid pressures at the first surface and on the second surface can substantially compensate. The pressure compensation can be designed in particular by the design of the first and second surfaces and by their relation to each other.

In an advantageous development, the second closing body does not close the drain opening when the inlet opening is closed. In this way, a vent can take place, which is required for an actuating movement of the closure element or supports it.

In an advantageous development of the closing body and the second closing body are arranged on a push rod of the electromagnet. In this case, the push rod can pass through the drain opening, wherein the second closing body is disposed beyond the pressure chamber. The closing body may also be referred to as a first closing body in the presence of a second closing body. The first closing body may be arranged separately from the push rod and bear against one end of the push rod. However, the first closing body can also be connected by means of ultrasonic welding to the push rod in order to be able to compensate for axial tolerances, for example.

In an advantageous embodiment, the second closing body or a drain port T comprises a check valve. The second closing body may be designed such that, when the position is closed, hydraulic fluid can not pass through the discharge opening in any direction. In the open position, however, an outflow is possible, but entry into the pressure chamber is prevented by the check valve. The second closing body can also form the check valve body as the closing body. The closing body can be guided in this case along the push rod and spring loaded in the open position of the second closing body are brought into contact with a sealing seat of the drain opening. Alternatively, for example, a check valve ball can be arranged in a bore, wherein the bore forms the drain port T. A check valve is required, for example, in the event that the drain port T is not in direct contact with the environment, but with the hydraulic fluid flow, which leaves the valve via the drain port A.

In an advantageous embodiment, the closure element comprises a hollow cylindrical piston. In particular, the cavity of the hollow cylindrical piston may be a channel or a bore, each extending from one axial end to a second axial end of the hollow cylindrical piston. The hollow space of the hollow cylindrical piston can advantageously form part of the hydraulic connection.

In an advantageous development of the hollow cylindrical piston carries on a front side, which faces the pressure chamber, a cup-shaped sleeve, wherein the cup-shaped sleeve forms the second surface of the closure element and wherein the cup-shaped sleeve has a recess as an inlet opening, through which the push rod with the closing body be upheld.

The arrangement of the closing body in the hydraulic connection ensures that in a non-actuated, ie in the de-energized or de-energized state of the electromagnet, the inlet opening can be closed only by hydraulic fluid pressure. The inlet opening is thus closed in an advantageous development with non-actuated solenoid valve by the closing body.

The design of the closure element with a hollow cylindrical piston and a cup-shaped sleeve allows a particularly cost-effective design. The cup-shaped sleeve can be formed, for example, as a formed part, in particular deep-drawing or extruded part, from sheet metal. Alternatively, the cup-shaped sleeve can also be made of plastic, in particular duroplastic.

Between the inner wall of the component, which receives the closure element (recording, in particular designed as a tubular housing), and the cup-shaped sleeve may be provided a tight clearance fit. The outer diameter of the cup-shaped sleeve thus forms the guide diameter of the closure element, which is characterized by a high accuracy and a small leakage gap.

The hollow cylindrical piston and the cup-shaped sleeve, however, may be aligned with each other with a loose clearance. This creates a surface between cup-shaped sleeve and recording, which is characterized by a good seal. The hollow cylindrical piston, however, can align itself with the position of the sealing seat and compensate for production-related coaxial errors.

The cup-shaped sleeve and the hollow cylindrical piston can be firmly connected. In particular, a groove can be provided on the outer circumference of the hollow cylindrical piston, into which an embossing of the cup-shaped sleeve engages. In addition to a positive connection and a non-positive connection, for example by means of a press fit, or an adhesive bond is conceivable.

The hollow cylindrical piston can be designed as a turned part and thus emerge from a cutting process. Alternatively, the hollow cylindrical piston can also be designed as extruded part or consist of plastic.

The hollow cylindrical piston may have a fuse, by means of which the push rod with the hollow cylindrical piston remains in communication. Such a captive can, for example, be designed such that a paragraph at the end facing the supply line holds the closing body in the hollow cylinder of the hollow cylinder. In particular, the closing body can not be fixedly connected to the push rod and bear against the push rod at the end face. In addition, the closing body can spring-loaded on the hollow cylindrical piston, in particular the paragraph can serve as a spring seat. It is ensured that the inlet opening remains closed even with vibrations, whereby unwanted circuits of the closure element can be avoided.

The valve seat may originate from a turning operation or be used as a component separate from the receptacle. When designed as a separate component, the surface properties can be specifically adapted to the respective application. The attachment of a separate component can be done for example by means of a press fit or a snap ring.

The spring plate can be a deep-drawn part. Alternatively, the spring plate can be integrally formed on the receptacle, for example, by a rotating machining. The push rod may consist of plastic or emerge from a cutting machining as a turned part.

The second closing body may be integrally formed on the push rod. Alternatively, however, a separate from the push rod design is possible. In this case, moreover, an application to the force of a spring offers, which presses the second closing body against the sealing seat of the drain opening.

In an advantageous development of the closing body has a conical or spherical shaped portion which is provided for sealing engagement with the inlet opening, and a cylindrically shaped portion which is guided on the inner peripheral surface of the hollow cylindrical piston, wherein a conically or spherically shaped Section extending flattening of the cylindrically shaped portion allows a hydraulic connection between supply line and inlet opening. A hydraulic connection between the first surface and the second surface can thus be produced in a structurally inexpensive manner. An end surface of the closing body, which faces the supply line, ensures a reliable admission with a hydraulic fluid pressure. In this way, a displacement of the push rod in the direction of the pressure chamber can be effected.

The device for controlling a hydraulic fluid supply can be used in particular for cooling a piston of an internal combustion engine. In this case, the inlet port communicates with the general engine oil circuit, supplying the engine with pressurized engine oil. The supply connection communicates with at least one nozzle, which acts on at least one piston of an internal combustion engine for cooling with engine oil. The device can also be used generally for controlling large engine oil volume flows at the same time comparatively small power consumption.

The invention will be explained below with reference to exemplary embodiments.

1 shows an exemplary embodiment of the device for controlling a hydraulic fluid supply;

2 illustrates the operating states I-VI of in 1 shown device;

3 shows an alternative embodiment of the device for controlling a hydraulic fluid supply;

4 shows a further alternative embodiment of the device for controlling a hydraulic fluid supply and

5 shows a detail X of the embodiment 4 ,

A possible embodiment of a device 1 to the control of a hydraulic fluid supply is in 1 shown. One with sealing rings 23 equipped, tubular housing 2 , Which at one axial end a pressed-in pressure piece 24 has at a second axial end an inlet port P and a radial supply port A, which is arranged in the region of the axial end. Between the inlet port P and the drain port A extends a supply line 3 using a hollow cylindrical piston 4 and a cup-shaped sleeve 5 comprehensive closure element 5a can be released or closed.

The closure element 5a is disposed between inlet port P and supply port A, wherein a first surface 6 of closure element 5a the supply line 3 facing and spring loaded with a sealing seat 7 can be planted. The closure element 5a can counteract the force of a spring 8th be moved to an open state, provided that on the first surface 6 attacking hydraulic fluid pressure exceeds a certain threshold. A vent T allows pressure equalization to the environment or to A.

A second surface 9 of the closure element 5a is the supply line 3 arranged away and limits a pressure chamber 10 , The pressure room 10 Can via a hydraulic connection 11 with the supply line 3 be brought into fluid communication with the hydraulic connection 11 a channel 12 is, passing through the hollow cylindrical piston 4 extends. The hydraulic connection is controlled 11 using a solenoid valve (not fully shown). The hydraulic connection 11 extends from the first surface 6 to the second surface 9 of the closure element 5a and flows through an inlet opening 13 the cup-shaped sleeve 5 in the pressure room 10 , The control of the hydraulic connection 11 takes place such that a closing body 14 of the solenoid valve, the inlet opening 13 releases or closes.

The pressure room 10 is through the tubular housing 2 as well as through the closure element 5a on the one hand and through a spring plate 15 on the other hand limited. The spring plate 15 is in the tubular housing 2 pressed in and serves as a spring seat for those in the pressure room 10 arranged spring 8th , The pressure room 10 points next to the inlet opening 13 a drain opening 16 on, using a second closing body 17 the electromagnet is closed.

The first closing body 14 and the second closing body 17 are on a pushrod 18 of the electromagnet arranged such that the first closing body 14 with closed drainage opening 16 the inlet opening 13 does not close. With closed inlet opening 13 whereas the second closing body closes 17 the drain opening 16 Not. The pushrod 17 passes through both the drain opening 16 as well as the inlet opening 13 , whereby the first closing body 14 in the canal 12 of the hollow cylindrical piston 4 is arranged.

The first closing body 14 has a conically shaped section 19 on, in sealing contact with the inlet opening 13 can be brought. There is also a cylindrically shaped section 20 located on the inner circumferential surface of the hollow cylindrical piston 4 is guided. A towards conically shaped section 19 extending flattening 21 of the cylindrically shaped portion 20 allows the hydraulic connection 11 between supply line 3 and inlet opening 13 , The supply line 3 facing there is an end face 22 the piston-shaped first closing body 14 wherein the surface is designed such that in the de-energized state of the solenoid valve, the piston-shaped first closing body 14 at the sealing surface of the inlet opening 13 is applied.

The 2 illustrates the operating states I-VI, which in each case depending on the system parameters of the solenoid valve - "energized" (on) or "de-energized" (off) - and the exemplary pressure difference - "less than or equal to 0.9 bar" or "greater than 0 , 9 bar "- set. The pressure difference refers to the hydraulic fluid pressure at the first surface and the ambient pressure.

The starting point is the operating state I with a pressure difference of less than or equal to 0.9 bar and with an electroless solenoid valve. At the first surface 6 Thus, although a hydraulic fluid pressure can be applied, a displacement of the closure element 5a against the force of the spring 8th however, this does not cause it. Due to the on the face 22 acting hydraulic fluid pressure is the closing body 14 at the inlet opening 13 on, so the pressure room 10 not supplied with hydraulic fluid. Inlet connection P and supply connection A are not connected to each other.

At an increase of the first surface 6 acting hydraulic medium pressure can set a pressure difference that is greater than 0.9 bar. The device is thus transferred from the first operating state to the operating state II. Due to the on the face 22 acting hydraulic fluid pressure and the still currentless solenoid valve is the closing body 14 still at the inlet opening 13 on, so the pressure room 10 not supplied with hydraulic fluid. Between inlet port P and supply port A is the supply line 3 Approved.

In operating state III, the closing process begins. In a further acting pressure difference greater than 0.9 bar, the electromagnet is energized, whereby the closing body 14 the inlet opening 13 to the pressure room 10 releases. About the flattening 21 on the cylindrical section 20 Hydraulic fluid enters the pressure chamber 10 , At the same time, the second closing body closes 17 the drain opening 16 of the pressure chamber 10 , In the pressure room 10 If a hydraulic fluid pressure builds up, whereby the pressure difference continues to be greater than 0.9 bar - the pressure in the pressure chamber 10 However, it is at the hydraulic fluid pressure in the region of the first surface 6 adjusted and the device is finally transferred to the operating state IV.

A powerless switching of the solenoid valve separates the pressure chamber 10 from the hydraulic fluid supply P. At the first surface 6 is still a hydraulic fluid pressure, which leads to a pressure difference greater than 0.9 bar. The pressure difference between the second surface 9 of the now open to the environment (to the tank port T or the supply port A) pressure chamber 10 and the first surface 6 leads to a reopening of the supply line 3 , Subsequently, the device is located 1 in the open state, which corresponds to the operating state VI.

The 3 shows an alternative embodiment of the device 1 to the control of a hydraulic fluid supply. The essential difference with otherwise the same function is that the second closing body 33 as a check valve 34 is designed. The second closing body 33 is on the pushrod 17 guided and with the force of a check valve spring 25 impinged on the second shooting body 33 against the drain hole 16 suppressed.

In 4 is another alternative embodiment with electromagnet 26 shown, which has substantially the same characteristics as those in 1 shown device 1 , The hollow cylindrical piston 4 has a paragraph in this variant 27 on, a falling out of not stuck with the pushrod 18 connected first closing body 14 prevented. The seal seat 7 is separate from the housing in this variant 2 formed - in this way, the axial position of the hollow cylindrical piston 4 and thus the threshold pressure required for opening can be set. The detail X of the 5 shows a check valve integrated into the drain connection 28 , A valve ball 29 prevents backflow of the draining hydraulic fluid, wherein the valve ball 29 by means of a plug 30 in a recording 31 is held. Lateral flattening 32 of the plug 30 allow a hydraulic connection with the environment.

LIST OF REFERENCE NUMBERS

1

 contraption

2

 casing

3

 supply line

4

 Hollow cylindrical piston

5

 Cup-shaped sleeve

5a

 closure element

6

 first surface

7

 sealing seat

8th

 feather

9

 second surface

10

 pressure chamber

11

 hydraulic connection

12

 channel

13

 inlet opening

14

 (first) closing body

15

 penholder

16

 drain hole

17

 second closing body

18

 pushrod

19

 conical section

20

 Cylindrical section

21

 flattening

22

 face

23

 poetry

24

 Pressure piece

25

 Check valve spring

26

 Solenoid valve

27

 paragraph

28

 check valve

29

 valve ball

30

 Plug

31

 admission

32

 flattening

33

 second closing body

34

 check valve

P

 inflow connection

A

 supply terminal

T

 Drain connection (tank)

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 2778364 A1 [0002]

Claims (10)

Contraption ( 1 to the control of a hydraulic fluid supply of an internal combustion engine comprising a supply line extending between an inlet connection P and a supply connection A ( 3 ) and a by means of a hydraulic medium pressure actuated closure element ( 5a ), which is arranged between inlet connection P and supply connection A and which, when a threshold pressure is exceeded, hydraulically connects the inlet connection P to the supply connection A, a first surface ( 6 ) of the closure element ( 5a ) of the supply line ( 3 ) and spring-loaded with a sealing seat ( 7 ) and wherein a second surface ( 9 ) of the closure element ( 5a ) of the supply line ( 3 ) is turned away and a pressure chamber ( 10 ), and comprising a solenoid valve ( 26 ), which is a hydraulic connection ( 11 ) between the supply line ( 3 ) and the pressure chamber ( 10 ), whereby the hydraulic connection ( 11 ) from the first surface ( 6 ) to the second surface ( 9 ), characterized in that the hydraulic connection ( 11 ) via an inlet opening ( 13 ) into the pressure chamber ( 10 ), wherein the inlet opening ( 13 ) by means of a closing body ( 14 ) of the solenoid valve ( 26 ) is closable. Apparatus according to claim 1, characterized in that the pressure chamber ( 10 ) a drain opening ( 16 ), which by means of a second closing body ( 17 ) of the solenoid valve ( 26 ) is closable. Device according to claim 2, characterized in that the closing body ( 17 ) with closed discharge opening ( 16 ) the inlet opening ( 13 ) does not close. Apparatus according to claim 2 or 3, characterized in that the second closing body ( 17 ) with closed inlet opening ( 13 ) the drain opening ( 16 ) does not close. Device according to one of claims 2 to 4, characterized in that the closing body ( 14 ) and the second closing body ( 17 ) on a push rod ( 18 ) of the solenoid valve ( 26 ) are arranged. Device according to one of claims 2 to 5, characterized in that the second closing body ( 33 ) a check valve ( 34 ) or that a drain port T a check valve ( 28 ). Device according to one of the preceding claims, characterized in that the closure element ( 5a ) a hollow cylindrical piston ( 4 ) and that the hollow cylindrical piston ( 4 ) on a front side, the pressure chamber ( 10 ), a cup-shaped sleeve ( 5 ), wherein the cup-shaped sleeve ( 5 ) the second surface ( 9 ) of the closure element ( 5a ) and wherein the cup-shaped sleeve ( 5 ) a recess as an inlet opening ( 13 ), through which the push rod ( 18 ) with the closing body ( 14 ) attacks. Device according to one of the preceding claims, characterized in that the inlet opening ( 13 ) with non-actuated solenoid valve ( 26 ) through the closing body ( 14 ) is closed. Device according to one of claims 7 to 8, characterized in that the closing body ( 14 ) a conically or spherically shaped portion ( 19 ), which for sealing engagement with the inlet opening ( 13 ) is provided, and a cylindrically shaped portion ( 20 ), which on the inner peripheral surface of the hollow cylindrical piston ( 4 ), with a conically or spherically shaped section (FIG. 19 ) extending flattening ( 21 ) of the cylindrically shaped portion ( 20 ) a hydraulic connection between supply line ( 3 ) and inlet opening ( 13 ) allows. Device according to claims 5 and 7, characterized in that the hydraulic connection ( 11 ) one between the first surface ( 6 ) and the second surface ( 9 ) extending stepped bore, wherein the closing body ( 14 ) separated from the push rod ( 18 ) is arranged and by means of the shoulder formed by the stepped bore ( 27 ) is held in the stepped bore.

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