HYDRAULIC CYLINDER RETARDER

Abstract

A hydraulic cylinder retarder includes a hydraulic cylinder mechanism, a hydraulic oil conveying mechanism and a hydraulic oil valve mechanism. A piston component of the hydraulic cylinder mechanism is connected to a transmission device. Resistance to the piston movement of the hydraulic cylinder mechanism is generated by the hydraulic oil conveying mechanism and the hydraulic oil valve mechanism, so as to reduce the operation speed of the transmission device.

Claims

1. A hydraulic cylinder retarder, comprising: a hydraulic cylinder mechanism including a piston component and a piston compression chamber, the piston component connected with a transmission device, the piston component configured to conduct a piston motion against the piston compression chamber; a hydraulic oil conveying mechanism including a hydraulic oil chamber and an oil conveying pipe, the oil conveying pipe connected with the hydraulic oil chamber and conveying a hydraulic oil to the hydraulic oil chamber; and a hydraulic oil valve mechanism including a unidirectional in-flow valve component and a unidirectional out-flow valve component, the unidirectional in-flow valve component connected between the piston compression chamber and the hydraulic oil chamber to allow the hydraulic oil to unidirectionally flow into the piston compression chamber through the unidirectional in-flow valve component, the unidirectional out-flow valve component connected between the piston compression chamber and the hydraulic oil chamber to allow the hydraulic oil to unidirectionally flow out with an out-flow sectional square measure from the piston compression chamber through the unidirectional out-flow valve component, wherein the out-flow sectional square measure is significantly smaller than a piston sectional square measure of the piston component, so as to produce a resistance force during the piston motion of the piston component, thereby slowing an operation speed of the transmission device.

2. The hydraulic cylinder retarder of claim 1, wherein, the unidirectional out-flow valve component is configured to allow an adjustability of the out-flow sectional square measure.

3. The hydraulic cylinder retarder of claim 1, further comprising a crank mechanism, the hydraulic cylinder retarder including at least two hydraulic cylinder mechanisms, at least two hydraulic oil conveying mechanisms, and at least two hydraulic oil valve mechanisms, the piston components of the at least two hydraulic cylinder mechanisms are combined to the crank mechanism at opposite phase angles thereof, respectively, such that when the piston component of one hydraulic cylinder mechanism carries out an expanding motion of the piston motion, the piston component of another hydraulic cylinder mechanism carries out a compression motion of the piston motion; the piston mechanism is connected with the transmission device through the crank mechanism.

4. The hydraulic cylinder retarder of claim 3, wherein, the hydraulic oil chamber comprises a primary oil chamber and a secondary oil chamber that are separated and do not communicate, the oil conveying pipe connected between the primary oil chamber of one hydraulic oil conveying mechanism and the secondary oil chamber of another hydraulic oil conveying mechanism.

5. The hydraulic cylinder retarder of claim 4, wherein, the unidirectional in-flow valve component of the hydraulic oil valve mechanism comprises a unidirectional in-flow valve member which is connected between the piston compression chamber and the primary oil chamber, so as to allow the hydraulic oil to unidirectionally flow to the piston compression chamber through the unidirectional in-flow valve member.

6. The hydraulic cylinder retarder of claim 5, wherein, the unidirectional out-flow valve component of the hydraulic oil valve mechanism comprises a plurality of unidirectional out-flow valve members connected between the piston compression chamber and the secondary oil chamber, so as to allow the hydraulic oil to unidirectionally flow out with an out-flow sectional square measure from the piston compression chamber through the plurality of unidirectional out-flow valve members, wherein the out-flow sectional square measure is smaller than an in-flow sectional square measure of the unidirectional in-flow valve member.

7. The hydraulic cylinder retarder of claim 6, wherein, the unidirectional out-flow valve member includes an external control switch for externally controlling an on and off status of the unidirectional out-flow valve member, so as to vary a size of the out-flow sectional square measure.

8. The hydraulic cylinder retarder of claim 4, wherein, the hydraulic oil conveying mechanism further comprises a unidirectional conveying valve member disposed on the oil conveying pipe, so as to allow the hydraulic oil to unidirectionally flow from the oil conveying pipe through the unidirectional conveying valve member to the primary oil chamber.

9. The hydraulic cylinder retarder of claim 1, wherein, the piston compression chamber of the hydraulic cylinder mechanism and the hydraulic oil chamber of the hydraulic oil conveying mechanism are disposed in the same hydraulic cylinder body.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0020] FIG. 1 is a schematic view illustrating the hydraulic cylinder retarder in accordance with an embodiment of the present invention.

[0021] FIG. 2 is a schematic view illustrating the hydraulic cylinder retarder of FIG. 1 after half an operation period thereof.

DETAILED DESCRIPTION OF THE INVENTION

[0022] Embodiments in accordance with the present invention are further illustrated by the following contents and the attached drawings.

[0023] As shown by FIG. 1 and FIG. 2, the embodiments of the present invention are illustrated. The illustration refers to one embodiment of the present invention and does not intent to limit the technical features of the present invention.

[0024] Referring by FIG. 1 and FIG. 2, a hydraulic cylinder retarder 100 in accordance with an embodiment of the present invention comprises a hydraulic cylinder mechanism 1 including a piston component 11 and a piston compression chamber 12, the piston component 11 connected with a transmission device T, the piston component 11 configured to conduct a piston motion against the piston compression chamber 12; a hydraulic oil conveying mechanism 2 including a hydraulic oil chamber 21 and an oil conveying pipe 22, the oil conveying pipe 22 connected with the hydraulic oil chamber 21 and conveying a hydraulic oil to the hydraulic oil chamber 21; and a hydraulic oil valve mechanism 3 including a unidirectional in-flow valve component 31 and a unidirectional out-flow valve component 32, the unidirectional in-flow valve component 31 connected between the piston compression chamber 12 and the hydraulic oil chamber 21 to allow the hydraulic oil to flow into the piston compression chamber 12 through the unidirectional in-flow valve component 31, the unidirectional out-flow valve component 32 connected between the piston compression chamber 12 and the hydraulic oil chamber 21 to allow the hydraulic oil to unidirectionally flow out with an out-flow sectional square measure from the piston compression chamber 12 through the unidirectional out-flow valve component 32, wherein the out-flow sectional square measure is significantly smaller than a piston sectional square measure of the piston component 11, so as to produce a resistance force during the piston motion of the piston component 11, thereby slowing an operation speed of the transmission device T.

[0025] Specifically, in the embodiment, the hydraulic cylinder retarder 100 further comprises a crank mechanism 4, two hydraulic cylinder mechanisms 1, 1a, two hydraulic oil conveying mechanisms 2, 2a, and two hydraulic oil valve mechanisms 3. The piston components 11, 11a of the two hydraulic cylinder mechanisms 1, 1a are combined to the the crank mechanism 4 at the opposite phase angles thereof. Therefore, when the piston component 11 of one hydraulic cylinder mechanism 1 carries out the expanding motion of the piston motion, the piston component 11a of the other hydraulic cylinder mechanism 1a carries out the compression motion of the piston motion (as shown in FIG. 1). Also, when the piston component 11 of one hydraulic cylinder mechanism 1 carries out the compression motion of the piston motion, the piston component 11a of the other hydraulic cylinder mechanism 1a carries out the expanding motion of the piston motion (as shown in FIG. 2). Notably, the intension of being combined “at the opposite phase angles” is to allow the different hydraulic cylinder mechanisms 1, 1a to be driven by the crank mechanism 4 to carry out different stages of the piston motion (such as the expanding motion and the compression motion) at the same time, respectively. Therefore, although the piston motions carried out by the different hydraulic cylinder mechanisms 1, 1a differ by half an operation period (phase angles differed by 180 degrees), the operation period difference is able to be moderated to one-third or one-fourth operation period or in other difference ratio. Further, the hydraulic cylinder mechanism, the hydraulic oil conveying mechanism, and the hydraulic oil valve mechanism are allowed to be provided in an amount of one or more than two, which are preferably combined to the crank mechanism at an equal phase angle difference, so as to provide an average resistance force during the whole operation period.

[0026] Referring to FIG. 1, when the piston component 11 of the hydraulic cylinder mechanism 1 carries out the expanding motion of the piston motion, the piston component 11 moves outward from the piston compression chamber 12, such that the space in the piston compression chamber 12 is increased, and the pressure thereof is decreased. In such status, due to an instantaneous pressure difference between the piston compression chamber 12 and the hydraulic oil chamber 21, the hydraulic oil flows to the piston compression chamber 12 through the unidirectional in-flow valve component 31 to recover the pressure balance.

[0027] Referring to FIG. 2, when the piston component 11 of the hydraulic cylinder mechanism 1 carries out the compression motion of the piston motion, the piston component 11 moves inward toward the piston compression chamber 12, such that the space in the piston compression chamber 12 is decreased, and the pressure thereof is increased. In such status, due to an instantaneous pressure difference between the piston compression chamber 12 and the hydraulic oil chamber 21, the hydraulic oil flows out from the piston compression chamber 12 through the unidirectional out-flow valve component 32 to recover the pressure balance.

[0028] During the aforementioned piston motion, when the piston component 11 moves with a higher speed, the pressure difference is larger, and the produced resistance force is larger. Also, when the out-flow section square measure of the hydraulic oil is smaller, due to the relatively small compressibility of the hydraulic oil and the limited increasing of the flowing speed, the recovering of the pressure balance will takes a longer time, and the resistance effect produced upon the piston motion is larger. Therefore, when the operation speed of the transmission device T is higher (such as when the vehicle moves on a long distance down grade slope or a steep slope), the resistance force imposed by the hydraulic cylinder retarder 100 is correspondingly increased. Under the effect of such resistance force and the running torque, the transmission device T tends to stably slow down.

[0029] Referring to FIG. 1 and FIG. 2, regarding the hydraulic cylinder retarder 100 in accordance with the embodiment of the present invention, the hydraulic oil chamber 21 includes a primary oil chamber 211 and a secondary oil chamber 212. The primary oil chamber 211 and the secondary oil chamber 212 are separated and do not communicate. The oil conveying pipe 22 is connected between the primary oil chamber 211 of one hydraulic oil conveying mechanism 2 and the secondary oil chamber 212a of the hydraulic oil chamber 21a of another hydraulic oil conveying mechanism 2a. The oil conveying pipe 22a of the other hydraulic oil conveying mechanism 2a is connected between the secondary oil chamber 212 of the hydraulic oil conveying mechanism 2 and the primary oil chamber 211a of the hydraulic oil chamber 21a of the hydraulic oil conveying mechanism 2a. According, in the embodiment, the hydraulic oil circulates between the two hydraulic oil conveying mechanisms 2, 2a, so that the hydraulic cylinder retarder 100 is not necessarily connected to an external hydraulic oil tank.

[0030] Referring to FIG. 1 and FIG. 2, regarding the hydraulic cylinder retarder 100 in accordance with the embodiment of the present invention, the unidirectional in-flow valve component 31 of the hydraulic oil valve mechanism 3 includes a unidirectional in-flow valve member 311, which is connected between the piston compression chamber 12 and the primary oil chamber 211, so as to allow the hydraulic oil to unidirectionally flow through the unidirectional in-flow valve member 311 to the piston compression chamber 12. The unidirectional in-flow valve member 311 in the embodiment is configured to provide sufficient in-flow sectional square measure, so as to lower additional resistance force which affects the piston motion.

[0031] Further, the unidirectional out-flow valve component 32 of the hydraulic oil valve mechanism 3 preferably includes a plurality of unidirectional out-flow valve members 321, 322 (which are provided in an amount of two in the drawings) that are connected between the piston compression chamber 12 and the secondary oil chamber 212, so as to allow the hydraulic oil to unidirectionally flow out with the out-flow sectional square measure from the piston compression chamber 12 through the plurality of unidirectional out-flow valve members 321, 322, wherein the summation of the out-flow sectional square measures of the plurality of unidirectional out-flow valve members 321, 322 is significantly smaller than a piston sectional square measure of the piston component. Preferably, the unidirectional out-flow valve members 321, 322 include an external control switch 320 for externally controlling an on and off status of the unidirectional out-flow valve members, respectively, so as to vary the size of the out-flow sectional square measure, thus adjusting the resistance force imposed by the hydraulic cylinder retarder 100 to the transmission device T.

[0032] Referring to FIG. 1 and FIG. 2, regarding the hydraulic cylinder retarder 100 in accordance with the embodiment of the present invention, the hydraulic oil conveying mechanism 2 further includes a unidirectional conveying valve member 23 disposed on the oil conveying pipe 22, so as to allow the hydraulic oil to unidirectionally flow to the primary oil chamber 211 through the unidirectional conveying valve member 23. By use of the unidirectional conveying valve member 23, the flowing of the hydraulic oil becomes smoother, so as to decrease the reflux in the pipe.

[0033] Referring to FIG. 1 and FIG. 2, regarding the hydraulic cylinder retarder 100 in accordance with the embodiment of the present invention, the piston compression chamber 12 of the hydraulic cylinder mechanism 1 and the hydraulic oil chamber 21 of the hydraulic oil conveying mechanism 2 are disposed in the same hydraulic cylinder body 10. Such configuration saves room and achieves a stronger structure, so as to improve the reliability and stability of the whole device. However, the manner of configuration is not limited to such arrangement. The piston compression chamber 12 and the hydraulic oil chamber 21 are allowed to be separately disposed.

[0034] With such configuration, the hydraulic cylinder retarder 100 applies the resistance force produced during the piston motion, so as to slow down the transmission device T. Also, with the direct proportion relationship between the resistance force and the operation speed of the transmission device T, steady slowing effect is achieved. The hydraulic cylinder retarder 100 applies the lubrication and cooling effect of the hydraulic oil, thus being prevented from being easily affected by heat generation. Also, the combination structure between the cylinder and the piston of the hydraulic cylinder retarder 100 is relatively simple, without comparatively delicate mechanical arrangement, thus being easy to be disposed, and the size thereof is minimized. Further, due to the volume compressibility of the hydraulic oil of the hydraulic cylinder retarder 100 being significantly small, a sufficient torque is efficiently and immediately produced even if the volume is relatively small, thereby achieving the slowing effect.

[0035] Although particular embodiments of the invention have been described in detail for purposes of illustration, various modifications and enhancements may be made without departing from the spirit and scope of the invention. Accordingly, the invention is not to be limited except as by the appended claims.